US20110132321A1 - Fuel Injector Diagnostic for Dual Fuel Engine - Google Patents

Fuel Injector Diagnostic for Dual Fuel Engine Download PDF

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US20110132321A1
US20110132321A1 US12/756,838 US75683810A US2011132321A1 US 20110132321 A1 US20110132321 A1 US 20110132321A1 US 75683810 A US75683810 A US 75683810A US 2011132321 A1 US2011132321 A1 US 2011132321A1
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fuel
injector
engine
rail
injection
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US12/756,838
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US8118006B2 (en
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Ross Dykstra Pursifull
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Ford Global Technologies LLC
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Ford Global Technologies LLC
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Assigned to FORD GLOBAL TECHNOLOGIES, LLC reassignment FORD GLOBAL TECHNOLOGIES, LLC ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: PURSIFULL, ROSS DYKSTRA
Priority to CN201110092533.3A priority patent/CN102213153B/en
Publication of US20110132321A1 publication Critical patent/US20110132321A1/en
Priority to US13/399,631 priority patent/US8364384B2/en
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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02DCONTROLLING COMBUSTION ENGINES
    • F02D41/00Electrical control of supply of combustible mixture or its constituents
    • F02D41/0025Controlling engines characterised by use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures
    • F02D41/0027Controlling engines characterised by use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures the fuel being gaseous
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02DCONTROLLING COMBUSTION ENGINES
    • F02D19/00Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures
    • F02D19/06Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures peculiar to engines working with pluralities of fuels, e.g. alternatively with light and heavy fuel oil, other than engines indifferent to the fuel consumed
    • F02D19/0602Control of components of the fuel supply system
    • F02D19/0607Control of components of the fuel supply system to adjust the fuel mass or volume flow
    • F02D19/061Control of components of the fuel supply system to adjust the fuel mass or volume flow by controlling fuel injectors
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02DCONTROLLING COMBUSTION ENGINES
    • F02D19/00Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures
    • F02D19/06Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures peculiar to engines working with pluralities of fuels, e.g. alternatively with light and heavy fuel oil, other than engines indifferent to the fuel consumed
    • F02D19/0623Failure diagnosis or prevention; Safety measures; Testing
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02DCONTROLLING COMBUSTION ENGINES
    • F02D41/00Electrical control of supply of combustible mixture or its constituents
    • F02D41/008Controlling each cylinder individually
    • F02D41/0082Controlling each cylinder individually per groups or banks
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02DCONTROLLING COMBUSTION ENGINES
    • F02D41/00Electrical control of supply of combustible mixture or its constituents
    • F02D41/22Safety or indicating devices for abnormal conditions
    • F02D41/221Safety or indicating devices for abnormal conditions relating to the failure of actuators or electrically driven elements
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02DCONTROLLING COMBUSTION ENGINES
    • F02D41/00Electrical control of supply of combustible mixture or its constituents
    • F02D41/30Controlling fuel injection
    • F02D41/38Controlling fuel injection of the high pressure type
    • F02D41/3809Common rail control systems
    • F02D41/3836Controlling the fuel pressure
    • F02D41/3845Controlling the fuel pressure by controlling the flow into the common rail, e.g. the amount of fuel pumped
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/02Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0225Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
    • F02M63/0275Arrangement of common rails
    • F02M63/0285Arrangement of common rails having more than one common rail
    • F02M63/029Arrangement of common rails having more than one common rail per cylinder bank, e.g. storing different fuels or fuels at different pressure levels per cylinder bank
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M69/00Low-pressure fuel-injection apparatus ; Apparatus with both continuous and intermittent injection; Apparatus injecting different types of fuel
    • F02M69/04Injectors peculiar thereto
    • F02M69/042Positioning of injectors with respect to engine, e.g. in the air intake conduit
    • F02M69/046Positioning of injectors with respect to engine, e.g. in the air intake conduit for injecting into both the combustion chamber and the intake conduit
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02DCONTROLLING COMBUSTION ENGINES
    • F02D19/00Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures
    • F02D19/06Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures peculiar to engines working with pluralities of fuels, e.g. alternatively with light and heavy fuel oil, other than engines indifferent to the fuel consumed
    • F02D19/0626Measuring or estimating parameters related to the fuel supply system
    • F02D19/0628Determining the fuel pressure, temperature or flow, the fuel tank fill level or a valve position
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02DCONTROLLING COMBUSTION ENGINES
    • F02D19/00Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures
    • F02D19/06Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures peculiar to engines working with pluralities of fuels, e.g. alternatively with light and heavy fuel oil, other than engines indifferent to the fuel consumed
    • F02D19/0663Details on the fuel supply system, e.g. tanks, valves, pipes, pumps, rails, injectors or mixers
    • F02D19/0686Injectors
    • F02D19/0689Injectors for in-cylinder direct injection
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02DCONTROLLING COMBUSTION ENGINES
    • F02D19/00Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures
    • F02D19/06Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures peculiar to engines working with pluralities of fuels, e.g. alternatively with light and heavy fuel oil, other than engines indifferent to the fuel consumed
    • F02D19/0663Details on the fuel supply system, e.g. tanks, valves, pipes, pumps, rails, injectors or mixers
    • F02D19/0686Injectors
    • F02D19/0692Arrangement of multiple injectors per combustion chamber
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02DCONTROLLING COMBUSTION ENGINES
    • F02D41/00Electrical control of supply of combustible mixture or its constituents
    • F02D41/22Safety or indicating devices for abnormal conditions
    • F02D2041/224Diagnosis of the fuel system
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02DCONTROLLING COMBUSTION ENGINES
    • F02D41/00Electrical control of supply of combustible mixture or its constituents
    • F02D41/30Controlling fuel injection
    • F02D41/38Controlling fuel injection of the high pressure type
    • F02D41/3809Common rail control systems
    • F02D2041/3881Common rail control systems with multiple common rails, e.g. one rail per cylinder bank, or a high pressure rail and a low pressure rail
    • YGENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02TCLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00Road transport of goods or passengers
    • Y02T10/10Internal combustion engine [ICE] based vehicles
    • Y02T10/30Use of alternative fuels, e.g. biofuels

Definitions

  • the present application relates to diagnosing injector variability in a fuel injection system in a dual fuel engine.
  • fuel injectors When new, fuel injectors may exhibit some piece-to-piece variability. Over time, injector performance may degrade (e.g., injector becomes clogged) which may further increase piece-to-piece injector variability. As a result, the actual amount of fuel injected to each cylinder of an engine may not be the desired amount and the difference between the actual and desired amounts may vary between injectors. Such discrepancies can lead to reduced fuel economy, increased tailpipe emissions, and an overall decrease in engine efficiency. Further, engines operating with a plurality of different injection substances, such as different fuel mixtures, may have even more fuel injectors (e.g., twice as many) resulting in a greater possibility for degradation of engine performance due to injector degradation.
  • a method for controlling fuel injection of a dual multi-substance injection engine which includes first and second fuel rails and first and second fuel pumps is disclosed.
  • the method comprises, suspending pumping of a second substance into the second fuel rail and injecting a first substance to all but a single cylinder of the engine, and, while pumping is suspended in the second fuel rail, injecting the second substance into the single cylinder and correlating pressure decrease in the second fuel rail to injector operation.
  • an injector By suspending pumping in the second fuel rail, an injector can be isolated and pressure drops in the fuel rail can be correlated to the operation of the injector. Further, injection of the first fuel can continue without interruption in all but one of the cylinders. In this manner, each fuel injector can be isolated and tested without significantly affecting engine operation.
  • FIG. 1 shows a schematic diagram of an engine.
  • FIG. 2 shows a schematic diagram of a dual fuel system.
  • FIG. 3 shows a flow chart illustrating a routine for
  • FIG. 4 shows a flow chart illustrating an example fuel injector diagnostic routine.
  • FIG. 5 shows a flow chart illustrating an example fuel pump diagnostic routine.
  • FIGS. 6A and 6B show an example fuel injection timing and fuel pressure change during a diagnostic routine.
  • FIGS. 7A and 7B show another example of fuel injection timing and fuel pressure change during a diagnostic routine.
  • a diagnostic routine may be carried out in the following manner: pumping of a second fuel into the second fuel rail is suspended while a first fuel is injected to all but a single cylinder of the engine. Further, while pumping is suspended in the second fuel rail, the second fuel is injected into the single cylinder and the pressure decrease in the second fuel rail is correlated to injector operation.
  • a single injector may be isolated at one time allowing the injector to be tested without having a substantial impact on the performance of the engine. Furthermore, all injectors for both types of fuel can be tested in this manner.
  • a sub-group of cylinders may be isolated together, rather than a single cylinder as noted above.
  • FIG. 1 shows one cylinder of a multi-cylinder engine, as well as the intake and exhaust path connected to that cylinder.
  • engine 10 is capable of using two different substances, and/or two different injectors in one example.
  • engine 10 may use gasoline and an alcohol containing fuel such as ethanol, methanol, a mixture of gasoline and ethanol (e.g., E85 which is approximately 85% ethanol and 15% gasoline), a mixture of gasoline and methanol (e.g., M85 which is approximately 85% methanol and 15% gas), etc.
  • engine 10 may use one fuel or fuel blend (e.g., gasoline or gasoline and ethanol) and one mixture of water and fuel (e.g., water and methanol).
  • engine 10 may use gasoline and a reformate fuel generated in a reformer coupled to the engine.
  • two fuel systems are used, but each uses the same fuel, such as gasoline.
  • a single injector (such as a direct injector) may be used to inject a mixture of gasoline and an alcohol based fuel, where the ratio of the two fuel quantities in the mixture may be adjusted by controller 12 via a mixing valve, for example.
  • two different injectors for each cylinder are used, such as port and direct injectors.
  • different sized injectors in addition to different locations and different fuels, may be used.
  • FIG. 1 shows one example fuel system with two fuel injectors per cylinder, for at least one cylinder. Further, each cylinder may have two fuel injectors. The two injectors may be configured in various locations, such as two port injectors, one port injector and one direct injector (as shown in FIG. 1 ), or others.
  • FIG. 1 it shows a dual injection system, where engine 10 has both direct and port fuel injection, as well as spark ignition.
  • Internal combustion engine 10 comprising a plurality of combustion chambers, is controlled by electronic engine controller 12 .
  • Combustion chamber 30 of engine 10 is shown including combustion chamber walls 32 with piston 36 positioned therein and connected to crankshaft 40 .
  • a starter motor (not shown) may be coupled to crankshaft 40 via a flywheel (not shown), or alternatively direct engine starting may be used.
  • piston 36 may include a recess or bowl (not shown) to help in forming stratified charges of air and fuel, if desired.
  • a flat piston may be used.
  • Combustion chamber, or cylinder, 30 is shown communicating with intake manifold 44 and exhaust manifold 48 via respective intake valves 52 a and 52 b (not shown), and exhaust valves 54 a and 54 b (not shown).
  • intake valves 52 a and 52 b not shown
  • exhaust valves 54 a and 54 b not shown
  • four valves per cylinder may be used, in another example, a single intake and single exhaust valve per cylinder may also be used. In still another example, two intake valves and one exhaust valve per cylinder may be used.
  • Combustion chamber 30 can have a compression ratio, which is the ratio of volumes when piston 36 is at bottom center to top center.
  • the compression ratio may be approximately 9:1.
  • the compression ratio may be increased. For example, it may be between 10:1 and 11:1 or 11:1 and 12:1, or greater.
  • Fuel injector 66 A is shown directly coupled to combustion chamber 30 for delivering injected fuel directly therein in proportion to the pulse width of signal dfpw received from controller 12 via electronic driver 68 . While FIG. 1 shows injector 66 A as a side injector, it may also be located overhead of the piston, such as near the position of spark plug 92 . Such a position may improve mixing and combustion due to the lower volatility of some alcohol based fuels. Alternatively, the injector may be located overhead and near the intake valve to improve mixing.
  • Fuel may be delivered to fuel injector 66 A by a high pressure fuel system (shown in FIG. 2 ) including a fuel tank, fuel pumps, and a fuel rail.
  • fuel may be delivered by a single stage fuel pump at lower pressure, in which case the timing of the direct fuel injection may be more limited during the compression stroke than if a high pressure fuel system is used.
  • the fuel tank (or tanks) may (each) have a pressure transducer providing a signal to controller 12 .
  • Fuel injector 66 B is shown coupled to intake manifold 44 , rather than directly to cylinder 30 . Fuel injector 66 B delivers injected fuel in proportion to the pulse width of signal pfpw received from controller 12 via electronic driver 68 . Note that a single driver 68 may be used for both fuel injection systems, or multiple drivers may be used. Fuel system 164 is also shown in schematic form delivering vapors to intake manifold 44 .
  • engine 10 may include fuel reformer 97 with storage tank 93 for supplying a gaseous fuel to one or both fuel injectors 66 a and 66 b.
  • Gaseous fuel may be supplied to one or both fuel injectors from storage tank 93 by way of pump 96 and check valve 82 .
  • Pump 96 pressurizes gaseous fuel supplied from fuel reformer 97 in storage tank 93 .
  • Check valve 82 limits flow of gaseous fuel from storage tank 93 to fuel reformer 97 when the output of pump 96 is at a lower pressure than storage tank 93 .
  • check valve 82 may be positioned upstream of pump 96 . In other embodiments, check valve 82 may be positioned in parallel with pump 96 .
  • check valve 82 may instead be an actively controlled valve.
  • the actively controlled valve would be opened when the pump is operating.
  • the control signal to pump 96 may be a simple on/off signal, for example.
  • the control signal may be a continuous variable voltage, current, pulsewidth, desired speed, or desired flowrate, etc.
  • pump 96 may be turned off, slowed down, or disabled with one or more bypass valves (not shown).
  • Fuel reformer 97 includes catalyst 72 and may further include optional electrical heater 98 for reforming alcohol supplied from fuel tank 91 .
  • Fuel reformer 97 is shown coupled to the exhaust system downstream of catalyst 70 and exhaust manifold 48 . However, fuel reformer 97 may be coupled to exhaust manifold 48 and located upstream of catalyst 70 . Fuel reformer 97 may use exhaust heat to drive an endothermic dehydrogenation of alcohol supplied by fuel tank 91 and to promote fuel reformation.
  • Intake manifold 44 is shown communicating with throttle body 58 via throttle plate 62 .
  • throttle plate 62 is coupled to electric motor 94 so that the position of elliptical throttle plate 62 is controlled by controller 12 via electric motor 94 .
  • This configuration may be referred to as electronic throttle control (ETC), which can also be utilized during idle speed control.
  • ETC electronic throttle control
  • a bypass air passageway is arranged in parallel with throttle plate 62 to control inducted airflow during idle speed control via an idle control by-pass valve positioned within the air passageway.
  • Exhaust gas sensor 76 is shown coupled to exhaust manifold 48 upstream of catalytic converter 70 (where sensor 76 can correspond to various different sensors).
  • sensor 76 may be any of many known sensors for providing an indication of exhaust gas air/fuel ratio such as a linear oxygen sensor, a UEGO, a two-state oxygen sensor, an EGO, a HEGO, or an HC or CO sensor.
  • sensor 76 is a two-state oxygen sensor that provides signal EGO to controller 12 which converts signal EGO into two-state signal EGOS.
  • a high voltage state of signal EGOS indicates exhaust gases are rich of stoichiometry and a low voltage state of signal EGOS indicates exhaust gases are lean of stoichiometry.
  • Signal EGOS may be used to advantage during feedback air/fuel control to maintain average air/fuel at stoichiometry during a stoichiometric homogeneous mode of operation. Further details of air-fuel ratio control are included herein.
  • Distributorless ignition system 88 provides ignition spark to combustion chamber 30 via spark plug 92 in response to spark advance signal SA from controller 12 .
  • Controller 12 may cause combustion chamber 30 to operate in a variety of combustion modes, including a homogeneous air/fuel mode and a stratified air/fuel mode by controlling injection timing, injection amounts, spray patterns, etc. Further, combined stratified and homogenous mixtures may be formed in the chamber. In one example, stratified layers may be formed by operating injector 66 A during a compression stroke. In another example, a homogenous mixture may be formed by operating one or both of injectors 66 A and 66 B during an intake stroke (which may be open valve injection). In yet another example, a homogenous mixture may be formed by operating one or both of injectors 66 A and 66 B before an intake stroke (which may be closed valve injection).
  • injectors 66 A and 66 B may be used during one or more strokes (e.g., intake, compression, exhaust, etc.). Even further examples may be where different injection timings and mixture formations are used under different conditions, as described below.
  • Controller 12 can control the amount of fuel delivered by fuel injectors 66 A and 66 B so that the homogeneous, stratified, or combined homogenous/stratified air/fuel mixture in chamber 30 can be selected to be at stoichiometry, a value rich of stoichiometry, or a value lean of stoichiometry.
  • Controller 12 is shown as a microcomputer, including microprocessor unit 102 , input/output ports 104 , an electronic storage medium for executable programs and calibration values shown as read only memory chip 106 in this particular example, random access memory 108 , keep alive memory 110 , and a conventional data bus.
  • Controller 12 is shown receiving various signals from sensors coupled to engine 10 , in addition to those signals previously discussed, including measurement of inducted mass air flow (MAF) from mass air flow sensor 100 coupled to throttle body 58 ; engine coolant temperature (ECT) from temperature sensor 112 coupled to cooling sleeve 114 ; a profile ignition pickup signal (PIP) from Hall effect sensor 118 coupled to crankshaft 40 ; and throttle position TP from throttle position sensor 120 ; absolute Manifold Pressure Signal MAP from sensor 122 ; an indication of knock from knock sensor 182 ; and an indication of absolute or relative ambient humidity from sensor 180 .
  • MAF mass air flow
  • ECT engine coolant temperature
  • PIP profile ignition pickup signal
  • TP throttle position sensor 120
  • absolute Manifold Pressure Signal MAP from sensor 122
  • an indication of knock from knock sensor 182 an indication of absolute or relative ambient humidity from sensor 180 .
  • Engine speed signal RPM is generated by controller 12 from signal PIP in a conventional manner and manifold pressure signal MAP from a manifold pressure sensor provides an indication of vacuum, or pressure, in the intake manifold. During stoichiometric operation, this sensor can give an indication of engine load. Further, this sensor, along with engine speed, can provide an estimate of charge (including air) inducted into the cylinder. In a one example, sensor 118 , which is also used as an engine speed sensor, produces a predetermined number of equally spaced pulses every revolution of the crankshaft.
  • camshaft 130 of engine 10 is shown communicating with rocker arms 132 and 134 for actuating intake valves 52 a, 52 b and exhaust valves 54 a, 54 b.
  • Camshaft 130 is directly coupled to housing 136 .
  • Housing 136 forms a toothed wheel having a plurality of teeth 138 .
  • Housing 136 is hydraulically coupled to crankshaft 40 via a timing chain or belt (not shown). Therefore, housing 136 and camshaft 130 rotate at a speed substantially equivalent to the crankshaft.
  • the relative position of camshaft 130 to crankshaft 40 can be varied by hydraulic pressures in advance chamber 142 and retard chamber 144 .
  • advance chamber 142 By allowing high pressure hydraulic fluid to enter advance chamber 142 , the relative relationship between camshaft 130 and crankshaft 40 is advanced.
  • intake valves 52 a, 52 b and exhaust valves 54 a, 54 b open and close at a time earlier than normal relative to crankshaft 40 .
  • retard chamber 144 the relative relationship between camshaft 130 and crankshaft 40 is retarded.
  • intake valves 52 a, 52 b, and exhaust valves 54 a, 54 b open and close at a time later than normal relative to crankshaft 40 .
  • teeth 138 being coupled to housing 136 and camshaft 130 , allow for measurement of relative cam position via cam timing sensor 150 providing signal VCT to controller 12 .
  • Teeth 1 , 2 , 3 , and 4 are preferably used for measurement of cam timing and are equally spaced (for example, in a V-8 dual bank engine, spaced 90 degrees apart from one another) while tooth 5 is preferably used for cylinder identification.
  • controller 12 sends control signals (LACT, RACT) to conventional solenoid valves (not shown) to control the flow of hydraulic fluid either into advance chamber 142 , retard chamber 144 , or neither.
  • Relative cam timing can be measured in a variety of ways.
  • the time, or rotation angle, between the rising edge of the PIP signal and receiving a signal from one of the plurality of teeth 138 on housing 136 gives a measure of the relative cam timing.
  • a measure of cam timing for a particular bank is received four times per revolution, with the extra signal used for cylinder identification.
  • Sensor 160 may also provide an indication of oxygen concentration in the exhaust gas via signal 162 , which provides controller 12 a voltage indicative of the 02 concentration.
  • sensor 160 can be a HEGO, UEGO, EGO, or other type of exhaust gas sensor. Also note that, as described above with regard to sensor 76 , sensor 160 can correspond to various different sensors.
  • FIG. 1 merely shows one cylinder of a multi-cylinder engine, and that each cylinder has its own set of intake/exhaust valves, fuel injectors, spark plugs, etc.
  • the engine may be coupled to a starter motor (not shown) for starting the engine.
  • the starter motor may be powered when the driver turns a key in the ignition switch on the steering column, for example.
  • the starter is disengaged after engine starting, for example, by engine 10 reaching a predetermined speed after a predetermined time.
  • an exhaust gas recirculation (EGR) system may be used to route a desired portion of exhaust gas from exhaust manifold 48 to intake manifold 44 via an EGR valve (not shown).
  • EGR exhaust gas recirculation
  • a portion of combustion gases may be retained in the combustion chambers by controlling exhaust valve timing.
  • FIG. 2 illustrates a fuel injection system 200 with a high pressure dual fuel rail system which may be the fuel system coupled to engine 10 in FIG. 1 , for example.
  • the system 200 may include fuel tanks 201 a and 201 b, low pressure (or lift) fuel pumps 202 a and 202 b that supply fuel from the fuel tanks 201 a and 201 b to high pressure fuel pumps 206 a and 206 b via low pressure passages 204 a and 204 b, respectively.
  • the high pressure fuel pumps 206 a and 206 b supply pressurized fuel to the high pressure fuel rails 210 a and 210 b via high pressure passages 208 a and 208 b, respectively.
  • the high pressure fuel rail 210 a supplies pressurized fuel to fuel injectors 214 a, 214 b, 214 c, and 214 d and the high pressure fuel rail 210 b supplies pressurized fuel to fuel injectors 214 e, 214 f, 214 g, and 214 h.
  • the fuel injectors inject fuels into engine cylinders 212 a, 212 b, 212 c, and 212 d located in an engine block 216 . Un-injected fuel may be returned to the fuel tanks 201 a and 201 b via respective fuel return passages (not shown).
  • the engine block 216 may be coupled to an intake pathway 222 with an intake air throttle 224 .
  • the system may further include a control unit 226 . Similar to control unit 12 in FIG. 1 , the control unit may be further coupled to various other sensors 252 and various actuators 254 (e.g., fuel injection actuator, spark ignition actuator, throttle valve actuator, etc) for sensing and controlling vehicle operating conditions.
  • the control unit 226 may sense engine speed, throttle position, intake temperature and/or pressure, exhaust temperature/pressure, mass air flow, engine coolant temperature, crank angle position, variable cam position, injection timing, spark ignition timing through appropriate sensors.
  • the control unit 226 may also control operations of intake and/or exhaust valves or throttles, engine cooling fan, spark ignition, injector, and fuel pumps to control engine operating conditions.
  • FIG. 2 shows additional details of the fuel injection system.
  • control unit 226 which may be an engine control unit, powertrain control unit, control system, a separate unit, or combinations of various control units.
  • the control unit 226 is shown in FIG. 2 as a microcomputer, including an input/output (I/O) port 228 , a central processing unit (CPU) 232 , an electronic storage medium for executable programs and calibration values shown as read only memory (ROM) chip 230 in this particular example, random access memory (RAM) 234 , keep alive memory (KAM) 136 , and a data bus.
  • I/O input/output
  • CPU central processing unit
  • ROM read only memory
  • RAM random access memory
  • KAM keep alive memory
  • the control unit 226 may receive signals from various sensors.
  • the control unit 226 may receive fuel pressure signals from the high pressure fuel rails 210 a and 210 b via respective fuel pressure sensors 220 a and 220 b located in the high pressure fuel rails 210 a and 210 b.
  • the control unit may further receive throttle opening angle signals (O A ) indicating the intake air throttle position via a throttle position sensor 238 , intake air flow signals (Q a ) from a mass air flow sensor 240 , engine speed signals (N e ) from engine speed sensor 242 , accelerator pedal position signal from a pedal 244 via an accelerator pedal position sensor 246 , crank angle sensor 248 , and engine coolant temperature (ECT) signals from engine temperature sensor 250 .
  • O A throttle opening angle signals
  • Q a intake air flow signals
  • N e engine speed signals
  • ECT engine coolant temperature
  • control unit 226 may also receive other signals from various other sensors 252 .
  • control unit 226 may receive a profile ignition pickup signal (PIP) from a Hall effect sensor (not shown) coupled to a crankshaft and a manifold pressure signal MAP from a manifold pressure sensor, as shown in FIG. 1 .
  • PIP profile ignition pickup signal
  • MAP manifold pressure signal
  • the control unit 226 may control operations of various vehicular components via various actuators 254 .
  • the control unit 226 may control the operation of the fuel injectors 214 a - h through respective fuel injector actuators (not shown) and high pressure fuel pumps 206 a and 206 b through respective high pressure fuel pump actuators (not shown).
  • the high pressure fuel pumps 206 a and 206 b may be coupled to and controlled by the control unit 226 as is shown in FIG. 2 .
  • the control unit 226 may regulate the amount or speed of fuel to be fed into the high pressure rails 210 a and 210 b by the high pressure fuel pumps 206 a and 206 b through respective high pressure fuel pump controls (not shown).
  • the control unit 226 may also completely stop fuel supply to the high pressure fuel rails 210 a and 210 b.
  • the high pressure fuel pumps 206 a and 206 b may contain one or more relief valves that decrease the fuel pressure in the high pressure fuel rails when the fuel pressure in the high pressure fuel rails 210 a and 210 b is higher than desired.
  • the injectors are coupled to engine cylinders in this example, in other examples, the injectors may be coupled to an intake pathway.
  • the fuel injectors that are directly coupled to engine cylinders may be located overhead of cylinder pistons (not shown) or located on the side of an engine cylinder.
  • the injectors 214 a - h may be operatively coupled to and controlled by a control unit, such as the control unit 226 , as is shown in FIG. 2 .
  • An amount of fuel injected from the injector and the injection timing may be determined by the control unit 226 from an engine map stored in the control unit 226 on the basis of engine speed (N e ) and/or intake throttle angle (Q A ), or engine load.
  • the injector may be controlled via controlling an electromagnetic valve coupled to the injector (not shown).
  • the injector may not inject all the fuel supplied to the injector and may return part of the fuel supplied to the fuel tank through a return path, such as a return passage (not shown).
  • the high pressure fuel rails 210 a and 210 b may also contain one or more temperature sensors for sensing the fuel temperature in the high pressure fuel rails 210 a and 210 b and one or more pressure sensors for sensing the fuel pressure in the high pressure fuel rails 210 a and 210 b. They may also contain one or more relief valves that when opened decrease the pressure in the high pressure fuel rails when it is greater than desired and return extra fuel back to the fuel tank via a fuel return passage.
  • the fuel passages may contain one or more filters, pumps, pressure sensors, temperature sensors, and/or relief valves.
  • the fuel passages may include one or multiple lines.
  • the intake pathway 222 may contain one or more air filters, turbochargers, and/or surge tanks.
  • the engine may contain one or more engine cooling fans, cooling circuits, spark ignitions, valves, and controls. The engine may be coupled to an exhaust pathway.
  • routine 300 determines if a diagnostic routine is desired based on which fuels are desired for engine operation and an amount of time since the last injector calibration. For example, during conditions in which both fuels are needed, a diagnostic routine may not be run since injection of one of the fuels is suspended one of the cylinders.
  • Engine operating conditions are determined. Engine operating conditions may include load, temperature, speed, etc.
  • routine 300 proceeds to 312 where it is determined if both fuels are desired for engine operation. For example, if the engine is operating at high load, injection of both fuels may be desired in order to continue operating at high load. As another example, the engine may be operating under low load conditions and the engine may operate using one or both fuels.
  • routine 300 moves to 318 and the current engine operation is continued and the routine ends.
  • routine 300 continues to 314 where it is determined if the time since the last injector calibration is greater than or equal to a predetermined threshold.
  • injector calibration may be desired one or more times per drive cycle, every other drive cycle, or after a predetermined number of miles is driven.
  • routine 300 ends. In contrast, if the time since the last injector calibration is greater than or equal to the predetermined threshold, routine 300 proceeds to 316 and an injector diagnostic routine is carried out, as will be described below with reference to FIG. 4 .
  • routine 400 suspends the pumping of fuel into one of the fuel rails and fuel is injected to a single cylinder or a group of cylinders at a time in order to detect a pressure drop due to the injection.
  • the other fuel rail pump may continue to supply fuel to the other fuel rail and other cylinders of the engine and the diagnostic routine may be carried out using one injector at a time thereby maintaining engine efficiency.
  • the fuel system may include a first fuel rail (e.g., fuel rail A) coupled to a first fuel pump (e.g., fuel pump A) which pumps a first fuel (e.g., fuel A) into the first fuel rail and a second fuel rail (e.g., fuel rail B) coupled to a second fuel pump (e.g., fuel pump B) which pumps a second fuel (e.g., fuel B) into the second fuel rail.
  • Fuel A and fuel B may be various fuels such as gasoline, ethanol, a gaseous reformate fuel, a blend of gasoline and an alcohol based fuel, a mixture of fuel and water, etc.
  • injection of fuel A is carried out in all but one of the cylinders of the engine at 412 of routine 400 .
  • fuel A is injected to all but a single cylinder.
  • fuel A may be injected to cylinders 2 , 3 , and 4 , but not cylinder 1 .
  • injection of fuel A may be suspended in a group of cylinders instead of a single cylinder, for example, fuel A may be injected to cylinders 1 , 2 , and 3 and not cylinders 4 , 5 , and 6 in a six cylinder engine example.
  • fuel B is injected to the single cylinder at 414 of routine 400 .
  • fuel B may be injected to the single cylinder in a predetermined sequence for a predetermined number of times.
  • FIG. 6A shows an example in which only one injector is fired in a sequence.
  • fuel B may be injected to more than one cylinder (but only one cylinder at a time) in a predetermined sequence.
  • FIG. 7A shows an example in which four different injectors are fired at different times in a sequence.
  • the pressure drop due to the injection of fuel in the single cylinder can be correlated to injector degradation at 416 of routine 400 and injector degradation is indicated at 418 of routine 400 .
  • injector degradation is indicated at 418 of routine 400 .
  • the injector may be partially plugged and less fuel is injected than desired.
  • the injector may be slow to open and less fuel is injected than desired.
  • the injector may be stuck open and more fuel is injected than desired.
  • the injector may be slow to close and more fuel is injected than desired.
  • routine 400 moves to 426 and routine 500 (e.g., a pump diagnostic routine) of FIG. 5 commences.
  • routine 500 e.g., a pump diagnostic routine
  • routine 400 proceeds to 422 and pumping of fuel B into fuel rail B is resumed.
  • routine 400 proceeds to 422 and pumping of fuel B into fuel rail B is resumed.
  • the amount of fuel injected to the single cylinder by the injector is adjusted based on the correlation. For example, if the amount of fuel injected by an injector is more than desired, the injector is calibrated such that less fuel is injected per injection (e.g., the injection is compensated by a correction coefficient) in order to compensate for the injector degradation and maintain the efficiency of the system.
  • routine 500 suspends injection in one of the fuel rails while pumping in the fuel rail is resumed (or continues). In this manner, pressure increase in the fuel rail can be correlated to the operation of the pump and pump degradation can be indicated.
  • the pump diagnostic routine is carried out after the injector diagnostic routine when the pressure in the fuel has decreased a known amount. However, in other embodiments, the pump diagnostic routine may be carried out before the injector diagnostic routine or independent of the injector diagnostic routine.
  • routine 500 injection of fuel A is resumed in the single cylinder.
  • injection of fuel B is suspended in the single cylinder. As such, all cylinders receive only fuel A during the pump diagnostic routine.
  • pressure increase in fuel rail B is correlated to fuel pump degradation and then pump degradation is indicated at 518 of routine 500 . For example, if the pressure increase in the fuel rail deviates from a predetermined or expected value, degradation is indicated. As an example, if pressure increase is less than expected, a fuel filter coupled to the fuel pump may be clogged or the pump may be leaking.
  • routine 500 continues to 520 where operation of fuel pump B is adjusted based on the correlation. For example, a calibration coefficient may be calculated and if the pump is pumping less fuel than desired into the fuel rail per pump stroke, pump operation may be adjusted by the calibration coefficient such that more fuel is pumped into the fuel rail per pump stroke. Further, a diagnostic code may be sent to the engine controller indicating degradation of the pump and the need for service, for example.
  • FIGS. 6A and 6B show an example of fuel injection timing 600 and corresponding fuel pressure change 610 in a fuel rail during an injector diagnostic routine in a four cylinder engine.
  • the fuel pressure in the fuel rail Prior to an injector diagnostic routine, the fuel pressure in the fuel rail is maintained at a normal operating pressure and normal pump strokes are issued.
  • fuel pressure in the fuel rail is increased (e.g., via more or larger pump strokes) before pumping is suspended. As shown, for each injection, the pressure in the fuel rail drops.
  • FIGS. 7A and 7B show another example of fuel injection timing 700 and corresponding fuel pressure change 710 during an injector diagnostic routine.
  • multiple injectors are tested during the injector diagnostic routine in a four cylinder engine.
  • all four injector are fired at different times and the corresponding fuel pressure profile 710 may be used to calculate a correction coefficient for each injector.
  • pumping may be suspended in one of the fuel rails allowing its injectors to be isolated for testing. Further, operation of the corresponding fuel pump may be subsequently assessed. As such, diagnostic routines for the fuel injectors and fuel pumps may be carried out without significantly interfering with engine operation.
  • control and estimation routines included herein can be used with various engine and/or vehicle system configurations.
  • the specific routines described herein may represent one or more of any number of processing strategies such as event-driven, interrupt-driven, multi-tasking, multi-threading, and the like.
  • various acts, operations, or functions illustrated may be performed in the sequence illustrated, in parallel, or in some cases omitted.
  • the order of processing is not necessarily required to achieve the features and advantages of the example embodiments described herein, but is provided for ease of illustration and description.
  • One or more of the illustrated acts or functions may be repeatedly performed depending on the particular strategy being used.
  • the described acts may graphically represent code to be programmed into the computer readable storage medium in the engine control system.

Abstract

Various systems and methods are described for controlling fuel injection of a dual fuel engine which includes first and second fuel rails and first and second fuel pumps. In one example, while pumping is suspended in the second fuel rail, the first fuel is injected to all but one cylinder of the engine and the second fuel is injected to the one cylinder in a predetermined sequence. As such, the fuel injector injecting to the one cylinder is isolated and its performance may be assessed without significantly affecting engine performance.

Description

    TECHNICAL FIELD
  • The present application relates to diagnosing injector variability in a fuel injection system in a dual fuel engine.
  • BACKGROUND AND SUMMARY
  • When new, fuel injectors may exhibit some piece-to-piece variability. Over time, injector performance may degrade (e.g., injector becomes clogged) which may further increase piece-to-piece injector variability. As a result, the actual amount of fuel injected to each cylinder of an engine may not be the desired amount and the difference between the actual and desired amounts may vary between injectors. Such discrepancies can lead to reduced fuel economy, increased tailpipe emissions, and an overall decrease in engine efficiency. Further, engines operating with a plurality of different injection substances, such as different fuel mixtures, may have even more fuel injectors (e.g., twice as many) resulting in a greater possibility for degradation of engine performance due to injector degradation.
  • The inventor herein has recognized the above problems and has devised an approach to at least partially address them. Thus, a method for controlling fuel injection of a dual multi-substance injection engine which includes first and second fuel rails and first and second fuel pumps is disclosed. The method comprises, suspending pumping of a second substance into the second fuel rail and injecting a first substance to all but a single cylinder of the engine, and, while pumping is suspended in the second fuel rail, injecting the second substance into the single cylinder and correlating pressure decrease in the second fuel rail to injector operation.
  • By suspending pumping in the second fuel rail, an injector can be isolated and pressure drops in the fuel rail can be correlated to the operation of the injector. Further, injection of the first fuel can continue without interruption in all but one of the cylinders. In this manner, each fuel injector can be isolated and tested without significantly affecting engine operation.
  • It should be understood that the summary above is provided to introduce in simplified form a selection of concepts that are further described in the detailed description. It is not meant to identify key or essential features of the claimed subject matter, the scope of which is defined uniquely by the claims that follow the detailed description. Furthermore, the claimed subject matter is not limited to implementations that solve any disadvantages noted above or in any part of this disclosure.
  • BRIEF DESCRIPTION OF THE DRAWINGS
  • FIG. 1 shows a schematic diagram of an engine.
  • FIG. 2 shows a schematic diagram of a dual fuel system.
  • FIG. 3 shows a flow chart illustrating a routine for
  • FIG. 4 shows a flow chart illustrating an example fuel injector diagnostic routine.
  • FIG. 5 shows a flow chart illustrating an example fuel pump diagnostic routine.
  • FIGS. 6A and 6B show an example fuel injection timing and fuel pressure change during a diagnostic routine.
  • FIGS. 7A and 7B show another example of fuel injection timing and fuel pressure change during a diagnostic routine.
  • DETAILED DESCRIPTION
  • The following description relates to a method for controlling fuel injection in a multi-injection substance engine, such as a dual fuel engine, which includes first and second fuel rails and first and second fuel pumps. In one example, a diagnostic routine may be carried out in the following manner: pumping of a second fuel into the second fuel rail is suspended while a first fuel is injected to all but a single cylinder of the engine. Further, while pumping is suspended in the second fuel rail, the second fuel is injected into the single cylinder and the pressure decrease in the second fuel rail is correlated to injector operation. In this manner, a single injector may be isolated at one time allowing the injector to be tested without having a substantial impact on the performance of the engine. Furthermore, all injectors for both types of fuel can be tested in this manner. In another example, a sub-group of cylinders may be isolated together, rather than a single cylinder as noted above.
  • FIG. 1 shows one cylinder of a multi-cylinder engine, as well as the intake and exhaust path connected to that cylinder. In the embodiment shown in FIG. 1, engine 10 is capable of using two different substances, and/or two different injectors in one example. For example, engine 10 may use gasoline and an alcohol containing fuel such as ethanol, methanol, a mixture of gasoline and ethanol (e.g., E85 which is approximately 85% ethanol and 15% gasoline), a mixture of gasoline and methanol (e.g., M85 which is approximately 85% methanol and 15% gas), etc. Further, as another example, engine 10 may use one fuel or fuel blend (e.g., gasoline or gasoline and ethanol) and one mixture of water and fuel (e.g., water and methanol). As another example, engine 10 may use gasoline and a reformate fuel generated in a reformer coupled to the engine. In another example, two fuel systems are used, but each uses the same fuel, such as gasoline. In still another embodiment, a single injector (such as a direct injector) may be used to inject a mixture of gasoline and an alcohol based fuel, where the ratio of the two fuel quantities in the mixture may be adjusted by controller 12 via a mixing valve, for example. In still another example, two different injectors for each cylinder are used, such as port and direct injectors. In even another embodiment, different sized injectors, in addition to different locations and different fuels, may be used.
  • FIG. 1 shows one example fuel system with two fuel injectors per cylinder, for at least one cylinder. Further, each cylinder may have two fuel injectors. The two injectors may be configured in various locations, such as two port injectors, one port injector and one direct injector (as shown in FIG. 1), or others.
  • Continuing with FIG. 1, it shows a dual injection system, where engine 10 has both direct and port fuel injection, as well as spark ignition. Internal combustion engine 10, comprising a plurality of combustion chambers, is controlled by electronic engine controller 12. Combustion chamber 30 of engine 10 is shown including combustion chamber walls 32 with piston 36 positioned therein and connected to crankshaft 40. A starter motor (not shown) may be coupled to crankshaft 40 via a flywheel (not shown), or alternatively direct engine starting may be used.
  • In one particular example, piston 36 may include a recess or bowl (not shown) to help in forming stratified charges of air and fuel, if desired. However, in an alternative embodiment, a flat piston may be used.
  • Combustion chamber, or cylinder, 30 is shown communicating with intake manifold 44 and exhaust manifold 48 via respective intake valves 52 a and 52 b (not shown), and exhaust valves 54 a and 54 b (not shown). Thus, while four valves per cylinder may be used, in another example, a single intake and single exhaust valve per cylinder may also be used. In still another example, two intake valves and one exhaust valve per cylinder may be used.
  • Combustion chamber 30 can have a compression ratio, which is the ratio of volumes when piston 36 is at bottom center to top center. In one example, the compression ratio may be approximately 9:1. However, in some examples where different fuels are used, the compression ratio may be increased. For example, it may be between 10:1 and 11:1 or 11:1 and 12:1, or greater.
  • Fuel injector 66A is shown directly coupled to combustion chamber 30 for delivering injected fuel directly therein in proportion to the pulse width of signal dfpw received from controller 12 via electronic driver 68. While FIG. 1 shows injector 66A as a side injector, it may also be located overhead of the piston, such as near the position of spark plug 92. Such a position may improve mixing and combustion due to the lower volatility of some alcohol based fuels. Alternatively, the injector may be located overhead and near the intake valve to improve mixing.
  • Fuel may be delivered to fuel injector 66A by a high pressure fuel system (shown in FIG. 2) including a fuel tank, fuel pumps, and a fuel rail. Alternatively, fuel may be delivered by a single stage fuel pump at lower pressure, in which case the timing of the direct fuel injection may be more limited during the compression stroke than if a high pressure fuel system is used. Further, while not shown, the fuel tank (or tanks) may (each) have a pressure transducer providing a signal to controller 12.
  • Fuel injector 66B is shown coupled to intake manifold 44, rather than directly to cylinder 30. Fuel injector 66B delivers injected fuel in proportion to the pulse width of signal pfpw received from controller 12 via electronic driver 68. Note that a single driver 68 may be used for both fuel injection systems, or multiple drivers may be used. Fuel system 164 is also shown in schematic form delivering vapors to intake manifold 44.
  • Further, engine 10 may include fuel reformer 97 with storage tank 93 for supplying a gaseous fuel to one or both fuel injectors 66 a and 66 b. Gaseous fuel may be supplied to one or both fuel injectors from storage tank 93 by way of pump 96 and check valve 82. Pump 96 pressurizes gaseous fuel supplied from fuel reformer 97 in storage tank 93. Check valve 82 limits flow of gaseous fuel from storage tank 93 to fuel reformer 97 when the output of pump 96 is at a lower pressure than storage tank 93. In some embodiments, check valve 82 may be positioned upstream of pump 96. In other embodiments, check valve 82 may be positioned in parallel with pump 96. Further, check valve 82 may instead be an actively controlled valve. In such an embodiment, the actively controlled valve would be opened when the pump is operating. The control signal to pump 96 may be a simple on/off signal, for example. In other examples, the control signal may be a continuous variable voltage, current, pulsewidth, desired speed, or desired flowrate, etc. Further, pump 96 may be turned off, slowed down, or disabled with one or more bypass valves (not shown).
  • Fuel reformer 97 includes catalyst 72 and may further include optional electrical heater 98 for reforming alcohol supplied from fuel tank 91. Fuel reformer 97 is shown coupled to the exhaust system downstream of catalyst 70 and exhaust manifold 48. However, fuel reformer 97 may be coupled to exhaust manifold 48 and located upstream of catalyst 70. Fuel reformer 97 may use exhaust heat to drive an endothermic dehydrogenation of alcohol supplied by fuel tank 91 and to promote fuel reformation.
  • Intake manifold 44 is shown communicating with throttle body 58 via throttle plate 62. In this particular example, throttle plate 62 is coupled to electric motor 94 so that the position of elliptical throttle plate 62 is controlled by controller 12 via electric motor 94. This configuration may be referred to as electronic throttle control (ETC), which can also be utilized during idle speed control. In an alternative embodiment (not shown), a bypass air passageway is arranged in parallel with throttle plate 62 to control inducted airflow during idle speed control via an idle control by-pass valve positioned within the air passageway.
  • Exhaust gas sensor 76 is shown coupled to exhaust manifold 48 upstream of catalytic converter 70 (where sensor 76 can correspond to various different sensors). For example, sensor 76 may be any of many known sensors for providing an indication of exhaust gas air/fuel ratio such as a linear oxygen sensor, a UEGO, a two-state oxygen sensor, an EGO, a HEGO, or an HC or CO sensor. In this particular example, sensor 76 is a two-state oxygen sensor that provides signal EGO to controller 12 which converts signal EGO into two-state signal EGOS. A high voltage state of signal EGOS indicates exhaust gases are rich of stoichiometry and a low voltage state of signal EGOS indicates exhaust gases are lean of stoichiometry. Signal EGOS may be used to advantage during feedback air/fuel control to maintain average air/fuel at stoichiometry during a stoichiometric homogeneous mode of operation. Further details of air-fuel ratio control are included herein.
  • Distributorless ignition system 88 provides ignition spark to combustion chamber 30 via spark plug 92 in response to spark advance signal SA from controller 12.
  • Controller 12 may cause combustion chamber 30 to operate in a variety of combustion modes, including a homogeneous air/fuel mode and a stratified air/fuel mode by controlling injection timing, injection amounts, spray patterns, etc. Further, combined stratified and homogenous mixtures may be formed in the chamber. In one example, stratified layers may be formed by operating injector 66A during a compression stroke. In another example, a homogenous mixture may be formed by operating one or both of injectors 66A and 66B during an intake stroke (which may be open valve injection). In yet another example, a homogenous mixture may be formed by operating one or both of injectors 66A and 66B before an intake stroke (which may be closed valve injection). In still other examples, multiple injections from one or both of injectors 66A and 66B may be used during one or more strokes (e.g., intake, compression, exhaust, etc.). Even further examples may be where different injection timings and mixture formations are used under different conditions, as described below.
  • Controller 12 can control the amount of fuel delivered by fuel injectors 66A and 66B so that the homogeneous, stratified, or combined homogenous/stratified air/fuel mixture in chamber 30 can be selected to be at stoichiometry, a value rich of stoichiometry, or a value lean of stoichiometry.
  • Controller 12 is shown as a microcomputer, including microprocessor unit 102, input/output ports 104, an electronic storage medium for executable programs and calibration values shown as read only memory chip 106 in this particular example, random access memory 108, keep alive memory 110, and a conventional data bus. Controller 12 is shown receiving various signals from sensors coupled to engine 10, in addition to those signals previously discussed, including measurement of inducted mass air flow (MAF) from mass air flow sensor 100 coupled to throttle body 58; engine coolant temperature (ECT) from temperature sensor 112 coupled to cooling sleeve 114; a profile ignition pickup signal (PIP) from Hall effect sensor 118 coupled to crankshaft 40; and throttle position TP from throttle position sensor 120; absolute Manifold Pressure Signal MAP from sensor 122; an indication of knock from knock sensor 182; and an indication of absolute or relative ambient humidity from sensor 180. Engine speed signal RPM is generated by controller 12 from signal PIP in a conventional manner and manifold pressure signal MAP from a manifold pressure sensor provides an indication of vacuum, or pressure, in the intake manifold. During stoichiometric operation, this sensor can give an indication of engine load. Further, this sensor, along with engine speed, can provide an estimate of charge (including air) inducted into the cylinder. In a one example, sensor 118, which is also used as an engine speed sensor, produces a predetermined number of equally spaced pulses every revolution of the crankshaft.
  • Continuing with FIG. 1, a variable camshaft timing system is shown. Specifically, camshaft 130 of engine 10 is shown communicating with rocker arms 132 and 134 for actuating intake valves 52 a, 52 b and exhaust valves 54 a, 54 b. Camshaft 130 is directly coupled to housing 136. Housing 136 forms a toothed wheel having a plurality of teeth 138. Housing 136 is hydraulically coupled to crankshaft 40 via a timing chain or belt (not shown). Therefore, housing 136 and camshaft 130 rotate at a speed substantially equivalent to the crankshaft. However, by manipulation of the hydraulic coupling as will be described later herein, the relative position of camshaft 130 to crankshaft 40 can be varied by hydraulic pressures in advance chamber 142 and retard chamber 144. By allowing high pressure hydraulic fluid to enter advance chamber 142, the relative relationship between camshaft 130 and crankshaft 40 is advanced. Thus, intake valves 52 a, 52 b and exhaust valves 54 a, 54 b open and close at a time earlier than normal relative to crankshaft 40. Similarly, by allowing high pressure hydraulic fluid to enter retard chamber 144, the relative relationship between camshaft 130 and crankshaft 40 is retarded. Thus, intake valves 52 a, 52 b, and exhaust valves 54 a, 54 b open and close at a time later than normal relative to crankshaft 40.
  • Continuing with the variable cam timing system, teeth 138, being coupled to housing 136 and camshaft 130, allow for measurement of relative cam position via cam timing sensor 150 providing signal VCT to controller 12. Teeth 1, 2, 3, and 4 are preferably used for measurement of cam timing and are equally spaced (for example, in a V-8 dual bank engine, spaced 90 degrees apart from one another) while tooth 5 is preferably used for cylinder identification. In addition, controller 12 sends control signals (LACT, RACT) to conventional solenoid valves (not shown) to control the flow of hydraulic fluid either into advance chamber 142, retard chamber 144, or neither.
  • Relative cam timing can be measured in a variety of ways. In general terms, the time, or rotation angle, between the rising edge of the PIP signal and receiving a signal from one of the plurality of teeth 138 on housing 136 gives a measure of the relative cam timing. For the particular example of a V-8 engine, with two cylinder banks and a five-toothed wheel, a measure of cam timing for a particular bank is received four times per revolution, with the extra signal used for cylinder identification.
  • Sensor 160 may also provide an indication of oxygen concentration in the exhaust gas via signal 162, which provides controller 12 a voltage indicative of the 02 concentration. For example, sensor 160 can be a HEGO, UEGO, EGO, or other type of exhaust gas sensor. Also note that, as described above with regard to sensor 76, sensor 160 can correspond to various different sensors.
  • As described above, FIG. 1 merely shows one cylinder of a multi-cylinder engine, and that each cylinder has its own set of intake/exhaust valves, fuel injectors, spark plugs, etc.
  • Also, in the example embodiments described herein, the engine may be coupled to a starter motor (not shown) for starting the engine. The starter motor may be powered when the driver turns a key in the ignition switch on the steering column, for example. The starter is disengaged after engine starting, for example, by engine 10 reaching a predetermined speed after a predetermined time. Further, in the disclosed embodiments, an exhaust gas recirculation (EGR) system may be used to route a desired portion of exhaust gas from exhaust manifold 48 to intake manifold 44 via an EGR valve (not shown). Alternatively, a portion of combustion gases may be retained in the combustion chambers by controlling exhaust valve timing.
  • FIG. 2 illustrates a fuel injection system 200 with a high pressure dual fuel rail system which may be the fuel system coupled to engine 10 in FIG. 1, for example. The system 200 may include fuel tanks 201 a and 201 b, low pressure (or lift) fuel pumps 202 a and 202 b that supply fuel from the fuel tanks 201 a and 201 b to high pressure fuel pumps 206 a and 206 b via low pressure passages 204 a and 204 b, respectively. The high pressure fuel pumps 206 a and 206 b supply pressurized fuel to the high pressure fuel rails 210 a and 210 b via high pressure passages 208 a and 208 b, respectively. The high pressure fuel rail 210 a supplies pressurized fuel to fuel injectors 214 a, 214 b, 214 c, and 214 d and the high pressure fuel rail 210 b supplies pressurized fuel to fuel injectors 214 e, 214 f, 214 g, and 214 h. The fuel injectors inject fuels into engine cylinders 212 a, 212 b, 212 c, and 212 d located in an engine block 216. Un-injected fuel may be returned to the fuel tanks 201 a and 201 b via respective fuel return passages (not shown). The engine block 216 may be coupled to an intake pathway 222 with an intake air throttle 224.
  • The system may further include a control unit 226. Similar to control unit 12 in FIG. 1, the control unit may be further coupled to various other sensors 252 and various actuators 254 (e.g., fuel injection actuator, spark ignition actuator, throttle valve actuator, etc) for sensing and controlling vehicle operating conditions. For example, the control unit 226 may sense engine speed, throttle position, intake temperature and/or pressure, exhaust temperature/pressure, mass air flow, engine coolant temperature, crank angle position, variable cam position, injection timing, spark ignition timing through appropriate sensors. The control unit 226 may also control operations of intake and/or exhaust valves or throttles, engine cooling fan, spark ignition, injector, and fuel pumps to control engine operating conditions.
  • FIG. 2 shows additional details of the fuel injection system. Specifically, FIG. 2 shows control unit 226, which may be an engine control unit, powertrain control unit, control system, a separate unit, or combinations of various control units. The control unit 226 is shown in FIG. 2 as a microcomputer, including an input/output (I/O) port 228, a central processing unit (CPU) 232, an electronic storage medium for executable programs and calibration values shown as read only memory (ROM) chip 230 in this particular example, random access memory (RAM) 234, keep alive memory (KAM) 136, and a data bus.
  • The control unit 226 may receive signals from various sensors. For example, the control unit 226 may receive fuel pressure signals from the high pressure fuel rails 210 a and 210 b via respective fuel pressure sensors 220 a and 220 b located in the high pressure fuel rails 210 a and 210 b. The control unit may further receive throttle opening angle signals (OA) indicating the intake air throttle position via a throttle position sensor 238, intake air flow signals (Qa) from a mass air flow sensor 240, engine speed signals (Ne) from engine speed sensor 242, accelerator pedal position signal from a pedal 244 via an accelerator pedal position sensor 246, crank angle sensor 248, and engine coolant temperature (ECT) signals from engine temperature sensor 250.
  • In addition to the signals mentioned above, the control unit 226 may also receive other signals from various other sensors 252. For example, the control unit 226 may receive a profile ignition pickup signal (PIP) from a Hall effect sensor (not shown) coupled to a crankshaft and a manifold pressure signal MAP from a manifold pressure sensor, as shown in FIG. 1.
  • The control unit 226 may control operations of various vehicular components via various actuators 254. For example, the control unit 226 may control the operation of the fuel injectors 214 a-h through respective fuel injector actuators (not shown) and high pressure fuel pumps 206 a and 206 b through respective high pressure fuel pump actuators (not shown).
  • The high pressure fuel pumps 206 a and 206 b may be coupled to and controlled by the control unit 226 as is shown in FIG. 2. The control unit 226 may regulate the amount or speed of fuel to be fed into the high pressure rails 210 a and 210 b by the high pressure fuel pumps 206 a and 206 b through respective high pressure fuel pump controls (not shown). The control unit 226 may also completely stop fuel supply to the high pressure fuel rails 210 a and 210 b. Furthermore, the high pressure fuel pumps 206 a and 206 b may contain one or more relief valves that decrease the fuel pressure in the high pressure fuel rails when the fuel pressure in the high pressure fuel rails 210 a and 210 b is higher than desired.
  • Although the injectors are coupled to engine cylinders in this example, in other examples, the injectors may be coupled to an intake pathway. The fuel injectors that are directly coupled to engine cylinders may be located overhead of cylinder pistons (not shown) or located on the side of an engine cylinder. The injectors 214 a-h may be operatively coupled to and controlled by a control unit, such as the control unit 226, as is shown in FIG. 2. An amount of fuel injected from the injector and the injection timing may be determined by the control unit 226 from an engine map stored in the control unit 226 on the basis of engine speed (Ne) and/or intake throttle angle (QA), or engine load. The injector may be controlled via controlling an electromagnetic valve coupled to the injector (not shown). The injector may not inject all the fuel supplied to the injector and may return part of the fuel supplied to the fuel tank through a return path, such as a return passage (not shown).
  • The high pressure fuel rails 210 a and 210 b may also contain one or more temperature sensors for sensing the fuel temperature in the high pressure fuel rails 210 a and 210 b and one or more pressure sensors for sensing the fuel pressure in the high pressure fuel rails 210 a and 210 b. They may also contain one or more relief valves that when opened decrease the pressure in the high pressure fuel rails when it is greater than desired and return extra fuel back to the fuel tank via a fuel return passage.
  • Various other modifications or adjustments may be made to the above example systems. For example, the fuel passages (e.g., 204 a, 204 b, 208 a, and 208 b) may contain one or more filters, pumps, pressure sensors, temperature sensors, and/or relief valves. The fuel passages may include one or multiple lines. There may be one or more fuel cooling systems. The intake pathway 222 may contain one or more air filters, turbochargers, and/or surge tanks. The engine may contain one or more engine cooling fans, cooling circuits, spark ignitions, valves, and controls. The engine may be coupled to an exhaust pathway.
  • Continuing to FIG. 3, a routine 300 for determining if a diagnostic routine should be run is illustrated. Specifically, routine 300 determines if a diagnostic routine is desired based on which fuels are desired for engine operation and an amount of time since the last injector calibration. For example, during conditions in which both fuels are needed, a diagnostic routine may not be run since injection of one of the fuels is suspended one of the cylinders.
  • At 310 of routine 300, engine operating conditions are determined. Engine operating conditions may include load, temperature, speed, etc.
  • Once the engine operation conditions are determined, routine 300 proceeds to 312 where it is determined if both fuels are desired for engine operation. For example, if the engine is operating at high load, injection of both fuels may be desired in order to continue operating at high load. As another example, the engine may be operating under low load conditions and the engine may operate using one or both fuels.
  • If it is determined that both fuels are desired, routine 300 moves to 318 and the current engine operation is continued and the routine ends. On the other hand, if it is determined that both fuels are not desired for operation (e.g., one or both fuels may be used, but both fuels are not needed for optimum engine efficiency), routine 300 continues to 314 where it is determined if the time since the last injector calibration is greater than or equal to a predetermined threshold. As examples, injector calibration may be desired one or more times per drive cycle, every other drive cycle, or after a predetermined number of miles is driven.
  • If the time since the last injector calibration is not greater than or equal to the predetermined threshold, routine 300 ends. In contrast, if the time since the last injector calibration is greater than or equal to the predetermined threshold, routine 300 proceeds to 316 and an injector diagnostic routine is carried out, as will be described below with reference to FIG. 4.
  • Continuing to FIG. 4, a diagnostic routine 400 for fuel injectors is illustrated. Specifically, routine 400 suspends the pumping of fuel into one of the fuel rails and fuel is injected to a single cylinder or a group of cylinders at a time in order to detect a pressure drop due to the injection. As such, the other fuel rail pump may continue to supply fuel to the other fuel rail and other cylinders of the engine and the diagnostic routine may be carried out using one injector at a time thereby maintaining engine efficiency.
  • At 410 of routine 400, pumping of fuel B is suspended in fuel rail B. For example, in a dual fuel system, the fuel system may include a first fuel rail (e.g., fuel rail A) coupled to a first fuel pump (e.g., fuel pump A) which pumps a first fuel (e.g., fuel A) into the first fuel rail and a second fuel rail (e.g., fuel rail B) coupled to a second fuel pump (e.g., fuel pump B) which pumps a second fuel (e.g., fuel B) into the second fuel rail. Fuel A and fuel B may be various fuels such as gasoline, ethanol, a gaseous reformate fuel, a blend of gasoline and an alcohol based fuel, a mixture of fuel and water, etc.
  • After the pumping of fuel B is suspended in fuel rail B, injection of fuel A is carried out in all but one of the cylinders of the engine at 412 of routine 400. For example, if pumping of fuel B is suspended in fuel rail B, fuel A is injected to all but a single cylinder. As an example, in a four cylinder engine, fuel A may be injected to cylinders 2, 3, and 4, but not cylinder 1. In some embodiments, injection of fuel A may be suspended in a group of cylinders instead of a single cylinder, for example, fuel A may be injected to cylinders 1, 2, and 3 and not cylinders 4, 5, and 6 in a six cylinder engine example.
  • Next, while the pumping of fuel B is suspended in fuel rail B and the injection of fuel A is carried out in all but a single cylinder of the engine, fuel B is injected to the single cylinder at 414 of routine 400. In some examples, fuel B may be injected to the single cylinder in a predetermined sequence for a predetermined number of times. For example, FIG. 6A shows an example in which only one injector is fired in a sequence. In other examples, fuel B may be injected to more than one cylinder (but only one cylinder at a time) in a predetermined sequence. As an example, FIG. 7A shows an example in which four different injectors are fired at different times in a sequence.
  • Because pumping has been suspended in fuel rail B, the amount of fuel, and thus the pressure, decreases with each injection, thus the pressure drop due to the injection of fuel in the single cylinder can be correlated to injector degradation at 416 of routine 400 and injector degradation is indicated at 418 of routine 400. For example, if the change in pressure (e.g., pressure drop) is lower than expected, the injector may be partially plugged and less fuel is injected than desired. In another example, if the pressure drop is lower than expected at small pulse widths (e.g., a short amount of time between each injection in the sequence), the injector may be slow to open and less fuel is injected than desired. In yet another example, if the pressure drop is higher than expected, the injector may be stuck open and more fuel is injected than desired. As another example, if the pressure drop is higher than expected at small pulse widths, the injector may be slow to close and more fuel is injected than desired.
  • At 420, it is determined if a pump diagnostic routine is desired. As with the injector diagnostic routine, it may be desired to run a pump diagnostic routine at predetermined intervals, for example, one or more times per drive cycle or after a predetermined number of miles are driven. If it is determined that a pump diagnostic routine is desired, routine 400 moves to 426 and routine 500 (e.g., a pump diagnostic routine) of FIG. 5 commences.
  • On the other hand, if it is determined that a pump diagnostic routine is not desired, routine 400 proceeds to 422 and pumping of fuel B into fuel rail B is resumed. Next, at 424, the amount of fuel injected to the single cylinder by the injector is adjusted based on the correlation. For example, if the amount of fuel injected by an injector is more than desired, the injector is calibrated such that less fuel is injected per injection (e.g., the injection is compensated by a correction coefficient) in order to compensate for the injector degradation and maintain the efficiency of the system.
  • Continuing to FIG. 5, a pump diagnostic routine 500 is shown. Specifically, routine 500 suspends injection in one of the fuel rails while pumping in the fuel rail is resumed (or continues). In this manner, pressure increase in the fuel rail can be correlated to the operation of the pump and pump degradation can be indicated. In this embodiment, the pump diagnostic routine is carried out after the injector diagnostic routine when the pressure in the fuel has decreased a known amount. However, in other embodiments, the pump diagnostic routine may be carried out before the injector diagnostic routine or independent of the injector diagnostic routine.
  • At 510 of routine 500, injection of fuel A is resumed in the single cylinder. Next, at 512, injection of fuel B is suspended in the single cylinder. As such, all cylinders receive only fuel A during the pump diagnostic routine.
  • Once injection of fuel B is suspended, pumping of fuel B into fuel rail B is resumed at 514 of routine 500. Next, at 516, pressure increase in fuel rail B is correlated to fuel pump degradation and then pump degradation is indicated at 518 of routine 500. For example, if the pressure increase in the fuel rail deviates from a predetermined or expected value, degradation is indicated. As an example, if pressure increase is less than expected, a fuel filter coupled to the fuel pump may be clogged or the pump may be leaking.
  • After fuel pump degradation is correlated to the pressure increase in the fuel rail, routine 500 continues to 520 where operation of fuel pump B is adjusted based on the correlation. For example, a calibration coefficient may be calculated and if the pump is pumping less fuel than desired into the fuel rail per pump stroke, pump operation may be adjusted by the calibration coefficient such that more fuel is pumped into the fuel rail per pump stroke. Further, a diagnostic code may be sent to the engine controller indicating degradation of the pump and the need for service, for example.
  • FIGS. 6A and 6B show an example of fuel injection timing 600 and corresponding fuel pressure change 610 in a fuel rail during an injector diagnostic routine in a four cylinder engine. In the example of FIGS. 6A and 6B only one injector is tested during the injector diagnostic routine. Prior to an injector diagnostic routine, the fuel pressure in the fuel rail is maintained at a normal operating pressure and normal pump strokes are issued. In some embodiments, as shown at 610, at the start of the injector diagnostic routine, fuel pressure in the fuel rail is increased (e.g., via more or larger pump strokes) before pumping is suspended. As shown, for each injection, the pressure in the fuel rail drops.
  • FIGS. 7A and 7B show another example of fuel injection timing 700 and corresponding fuel pressure change 710 during an injector diagnostic routine. In the example of FIGS. 7A and 7B, multiple injectors are tested during the injector diagnostic routine in a four cylinder engine. In the sequence shown at 700, all four injector are fired at different times and the corresponding fuel pressure profile 710 may be used to calculate a correction coefficient for each injector.
  • Thus, during engine operating conditions in which both fuels are not desired for operation (e.g., one or both fuels may be used), pumping may be suspended in one of the fuel rails allowing its injectors to be isolated for testing. Further, operation of the corresponding fuel pump may be subsequently assessed. As such, diagnostic routines for the fuel injectors and fuel pumps may be carried out without significantly interfering with engine operation.
  • Note that the example control and estimation routines included herein can be used with various engine and/or vehicle system configurations. The specific routines described herein may represent one or more of any number of processing strategies such as event-driven, interrupt-driven, multi-tasking, multi-threading, and the like. As such, various acts, operations, or functions illustrated may be performed in the sequence illustrated, in parallel, or in some cases omitted. Likewise, the order of processing is not necessarily required to achieve the features and advantages of the example embodiments described herein, but is provided for ease of illustration and description. One or more of the illustrated acts or functions may be repeatedly performed depending on the particular strategy being used. Further, the described acts may graphically represent code to be programmed into the computer readable storage medium in the engine control system.
  • It will be appreciated that the configurations and routines disclosed herein are exemplary in nature, and that these specific embodiments are not to be considered in a limiting sense, because numerous variations are possible. For example, the above technology can be applied to V-6, I-4, I-6, V-12, opposed 4, and other engine types. The subject matter of the present disclosure includes all novel and nonobvious combinations and subcombinations of the various systems and configurations, and other features, functions, and/or properties disclosed herein.
  • The following claims particularly point out certain combinations and subcombinations regarded as novel and nonobvious. These claims may refer to “an” element or “a first” element or the equivalent thereof. Such claims should be understood to include incorporation of one or more such elements, neither requiring nor excluding two or more such elements. Other combinations and subcombinations of the disclosed features, functions, elements, and/or properties may be claimed through amendment of the present claims or through presentation of new claims in this or a related application.
  • Such claims, whether broader, narrower, equal, or different in scope to the original claims, also are regarded as included within the subject matter of the present disclosure.

Claims (20)

1. A method for controlling fuel injection of a multi-substance injection engine which includes first and second rails and first and second pumps, comprising:
suspending pumping of a second substance into the second rail and injecting a first substance to all but a single cylinder of the engine; and
while pumping is suspended in the second rail, injecting the second substance into the single cylinder and correlating pressure decrease in the second rail to injector operation.
2. The method of claim 1, wherein injector degradation is indicated when the pressure decrease is less than a predetermined value.
3. The method of claim 1, wherein injector degradation is indicated when the pressure decrease is greater than a predetermined value.
4. The method of claim 1, further comprising:
resuming injection of the first substance to the single cylinder and suspending injection of the second substance; and
while injection of the second substance is suspended, resuming pumping of the second substance to the second rail and correlating pressure increase in the second rail to operation of the second pump.
5. The method of claim 4, wherein degradation of the second pump is indicated when the pressure increase deviates from a predetermined value.
6. The method of claim 1, wherein one of the substances is a gaseous fuel generated in a reformer coupled to the vehicle.
7. The method of claim 1, wherein the second substance is injected to the single cylinder through a predetermined number of injections.
8. A method for controlling fuel injection of a dual fuel engine which includes first and second fuel rails and first and second fuel pumps, comprising:
suspending pumping of a second fuel into the second fuel rail and injecting a first fuel to all but a first group of cylinders of the engine;
while pumping is suspended in the second fuel rail, injecting the second fuel into the first group of cylinders, and correlating pressure decrease in the second fuel rail to injector operation; and
adjusting fuel injection of the second fuel in the first group of cylinders based on the correlation once pumping of the second fuel is resumed by the second pump.
9. The method of claim 8, wherein injector degradation is indicated when the pressure decrease deviates from a predetermined value, and wherein the first group of cylinders is a single cylinder.
10. The method of claim 8, further comprising:
resuming injection of the first fuel to the first group of cylinders and suspending injection of the second fuel;
while injection of the second fuel is suspended, resuming pumping of the second fuel to the second fuel rail and correlating pressure increase in the second fuel rail to operation of the second fuel pump; and
adjusting operation of the second fuel pump based on the correlation of pressure increase and pump operation.
11. The method of claim 10, wherein pump degradation is indicated when the pressure deviates from a predetermined value.
12. The method of claim 8, wherein the first fuel is gasoline and the second fuel is ethanol.
13. A system for an engine in a vehicle, comprising:
a plurality of cylinders, each cylinder having a first and second injector where the first injector is coupled to a first fuel rail and the second injector is coupled to a second fuel rail; and
a control system comprising a computer readable storage medium, the medium comprising instructions for:
during a first condition, injecting fuel to all cylinders via the first injectors; and p2 during a second condition:
injecting fuel to all but one cylinder via the first injectors, and injecting fuel to the one cylinder via only the second injector; and
suspending pumping of fuel into the second fuel rail while continuing pumping of fuel into the first fuel rail.
14. The system of claim 13, wherein the first injectors inject a first fuel and the second injectors inject a second fuel.
15. The system of claim 14, wherein the first condition includes operating conditions in which only one fuel is used and a diagnostic routine is not being carried out.
16. The system of claim 14, wherein the second condition includes operating conditions in which both fuels are used and a diagnostic routine is being carried out.
17. The system of claim 14, further comprising instructions for, during a third condition, injecting all cylinders via the first and second injectors.
18. The system of claim 17, wherein in the third condition includes operating conditions in which both fuels are used.
19. The system of claim 13, further comprising, during the second condition and while pumping is suspended in the second fuel rail, correlating pressure decrease in the second fuel rail to injector operation.
20. The system of claim 19, wherein degradation of the injector is indicated when the pressure decrease deviates from a predetermined value.
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Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20120222400A1 (en) * 2011-03-04 2012-09-06 General Electric Company Methods and systems for emissions control in a dual fuel engine
US20120240669A1 (en) * 2011-03-25 2012-09-27 Denso Corporation Abnormality determination apparatus and abnormality determination method for multi-cylinder internal combustion engine
US8360015B2 (en) 2010-04-08 2013-01-29 Ford Global Technologies, Llc Engine fuel reformer monitoring
US20130151114A1 (en) * 2011-12-09 2013-06-13 Hyundai Motor Company Method of managing auxiliary fuel system for ffv
EP2653706A1 (en) * 2012-04-20 2013-10-23 Caterpillar Motoren GmbH & Co. KG Monitoring the fuel injection system of dual fuel engines
US20140238353A1 (en) * 2013-02-27 2014-08-28 Caterpillar Inc. Apparatus and Method for Detecting Leakage of Liquid Fuel into Gas Fuel Rail
US20140290597A1 (en) * 2013-03-28 2014-10-02 Ford Global Technologies, Llc Method for operating a direct fuel injector
US20140311453A1 (en) * 2013-04-19 2014-10-23 Liebherr Machines Bulle Sa Controller for a Common-Rail Injection System
US20150243109A1 (en) * 2014-02-25 2015-08-27 Ford Global Technologies, Llc Method for triggering a vehicle system monitor
EP2853713A3 (en) * 2013-09-26 2016-03-23 Man Diesel & Turbo, Filial Af Man Diesel & Turbo Se, Tyskland A large low-speed tubocharged two-stroke internal combustion engine with a dual fuel supply system
EP2787200A4 (en) * 2011-11-30 2016-03-30 Aisan Ind Fuel supply control apparatus for bi-fuel internal combustion engine, and method of switching fuel in bi-fuel internal combustion engine
US9347386B2 (en) 2012-03-30 2016-05-24 Monsanto Technology Llc Alcohol reforming system for internal combustion engine
EP2999879A4 (en) * 2013-05-23 2017-02-15 Scania CV AB Method and device for operation of a high pressure fuel pump
RU2701430C2 (en) * 2014-09-18 2019-09-26 Форд Глобал Текнолоджиз, Ллк Method of determining fuel injector operation characteristic
US10450193B2 (en) 2012-03-30 2019-10-22 Monsanto Technology Llc Alcohol reformer for reforming alcohol to mixture of gas including hydrogen
US11873776B1 (en) * 2022-08-02 2024-01-16 Caterpillar Inc. Fuel injector drive system

Families Citing this family (31)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8245671B2 (en) 2010-04-08 2012-08-21 Ford Global Technologies, Llc Operating an engine with reformate
US8041500B2 (en) 2010-04-08 2011-10-18 Ford Global Technologies, Llc Reformate control via accelerometer
US8230826B2 (en) 2010-04-08 2012-07-31 Ford Global Technologies, Llc Selectively storing reformate
US8146541B2 (en) 2010-04-08 2012-04-03 Ford Global Technologies, Llc Method for improving transient engine operation
US8307790B2 (en) 2010-04-08 2012-11-13 Ford Global Technologies, Llc Method for operating a vehicle with a fuel reformer
US8191514B2 (en) 2010-04-08 2012-06-05 Ford Global Technologies, Llc Ignition control for reformate engine
WO2012051122A2 (en) * 2010-10-10 2012-04-19 Bex America, Llc Method and apparatus for converting diesel engines to blended gaseous and diesel fuel engines
US8789513B2 (en) 2011-09-26 2014-07-29 Hitachi, Ltd Fuel delivery system
WO2013055673A1 (en) * 2011-10-12 2013-04-18 Massachusetts Institute Of Technology Reformer enhanced alcohol engine
US9080517B2 (en) 2011-10-20 2015-07-14 Ford Global Technologies, Llc System and method for supplying fuel to an engine via multiple fuel paths
BR112014013289B1 (en) * 2011-12-08 2021-04-06 Toyota Jidosha Kabushiki Kaisha CONTROL DEVICE FOR INTERNAL COMBUSTION ENGINE
EP2634401B1 (en) * 2012-02-28 2014-11-05 Caterpillar Motoren GmbH & Co. KG Control system and method for dual fuel engines
US9115664B2 (en) * 2012-08-22 2015-08-25 Cummins Inc. Engine control systems and methods
US9228510B2 (en) 2012-08-22 2016-01-05 Cummins Inc. Engine control systems and methods
WO2014056103A1 (en) * 2012-10-09 2014-04-17 Westport Power Inc. Fuel system protection in a multi-fuel internal combustion engine
US9903306B2 (en) * 2013-02-08 2018-02-27 Cummins Inc. System and method for acquiring pressure data from a fuel accumulator of an internal combustion engine
CN103306839B (en) * 2013-07-01 2015-09-09 潍柴动力股份有限公司 The controlling method of rail pressure of common rail and control system
US9839877B2 (en) 2013-10-10 2017-12-12 Cummins Emission Solutions Inc. Reagent doser diagnostic system and method
US8920757B1 (en) 2013-10-24 2014-12-30 Cummins Emission Solutions Inc. Reductant dosing control systems and methods
US9593637B2 (en) 2013-12-05 2017-03-14 Ford Global Technologies, Llc Method of diagnosing injector variability in a multiple injector system
US9334824B2 (en) 2014-02-27 2016-05-10 Ford Global Technologies, Llc Method and system for characterizing a port fuel injector
US9617940B2 (en) * 2014-08-14 2017-04-11 General Electric Company Engine diagnostic system and an associated method thereof
US9556809B2 (en) 2014-12-12 2017-01-31 General Electric Company System and method for optimal fueling of an engine
DE102015002961A1 (en) * 2015-03-07 2016-09-08 Man Diesel & Turbo Se Method and control for operating a dual-fuel engine
US9599060B2 (en) 2015-07-21 2017-03-21 Ford Global Technologies, Llc Method for operating a fuel injection system
US10337445B2 (en) * 2015-07-21 2019-07-02 Ford Global Technologies, Llc Method for operating a dual fuel injection system
EP3387237B1 (en) * 2015-12-07 2019-11-20 Volvo Truck Corporation A method for controlling an internal combustion engine
JP6610567B2 (en) * 2017-01-16 2019-11-27 トヨタ自動車株式会社 Engine equipment
US9752515B1 (en) 2017-04-03 2017-09-05 James A. Stroup System, method, and apparatus for injecting a gas in a diesel engine
JP6869475B2 (en) * 2017-05-12 2021-05-12 アイシン精機株式会社 Internal combustion engine control device
CN112819991A (en) * 2021-01-11 2021-05-18 浙江吉利控股集团有限公司 Fault processing method for dual-fuel automobile, terminal and storage medium

Citations (68)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5176122A (en) * 1990-11-30 1993-01-05 Toyota Jidosha Kabushiki Kaisha Fuel injection device for an internal combustion engine
US5224452A (en) * 1991-09-12 1993-07-06 Japan Electronic Control Systems Co., Ltd. Air-fuel ratio control system of internal combustion engine
US5372411A (en) * 1992-04-13 1994-12-13 Robert Bosch Gmbh Safety equipment for a motor vehicle
US5445019A (en) * 1993-04-19 1995-08-29 Ford Motor Company Internal combustion engine with on-board diagnostic system for detecting impaired fuel injectors
US5526797A (en) * 1994-01-07 1996-06-18 Stokes; Richard A. Methods and apparatus for vaporizing and utilizing fuels of various octane ratings
US5528901A (en) * 1994-03-01 1996-06-25 Auxiliary Power Dynamics, Inc. Compact auxiliary power system for heavy-duty diesel engines and method
US5542394A (en) * 1994-04-15 1996-08-06 Unisia Jecs Corporation Vehicle engine refueling detection apparatus and method and fuel supply apparatus and method
US5633458A (en) * 1996-01-16 1997-05-27 Ford Motor Company On-board fuel delivery diagnostic system for an internal combustion engine
US5682864A (en) * 1995-08-01 1997-11-04 Nissan Motor Co., Ltd. Controller for internal combustion engines
US5740667A (en) * 1994-12-15 1998-04-21 Amoco Corporation Process for abatement of nitrogen oxides in exhaust from gas turbine power generation
US5762366A (en) * 1995-12-29 1998-06-09 Autoliv Asp, Inc. Safety system
US5857445A (en) * 1995-08-24 1999-01-12 Hitachi, Ltd. Engine control device
US5964088A (en) * 1996-03-22 1999-10-12 Toyota Jidosha Kabushiki Kaisha Device for purifying exhaust gas of engine
US6024069A (en) * 1997-06-02 2000-02-15 Nissan Motor Co., Ltd. Controller for an internal combustion engine
US6047542A (en) * 1995-11-17 2000-04-11 Toyota Jidosha Kabushiki Kaisha Method and device for purifying exhaust gas of engine
US6058906A (en) * 1997-07-02 2000-05-09 Nissan Motor Co., Ltd. Fuel/air ratio control for internal combustion engine
US6088647A (en) * 1997-09-16 2000-07-11 Daimlerchrysler Ag Process for determining a fuel-injection-related parameter for an internal-combustion engine with a common-rail injection system
US6176215B1 (en) * 1997-07-18 2001-01-23 Daimler Benz Aktiengesellschaft Method for operation of a direct-injection spark-ignition internal combustion engine
US6213104B1 (en) * 1996-02-14 2001-04-10 Toyota Jidosha Kabushiki Kaisha Method and a device for supplying fuel to an internal combustion engine
US6244043B1 (en) * 1999-05-19 2001-06-12 Ford Global Technologies, Inc. Emission control device air/fuel ratio control system
US6247449B1 (en) * 1995-12-22 2001-06-19 Ab Volvo Method for reducing vibration in a vehicle and a device for accomplishment of the method
US20010003977A1 (en) * 1999-12-13 2001-06-21 Kenji Hayashi Fuel injection system for internal combustion engines and its method of control
US6289672B1 (en) * 1998-07-21 2001-09-18 Toyota Jidosha Kabushiki Kaisha Exhaust gas purification device for an internal combustion engine
US6318306B1 (en) * 1999-04-06 2001-11-20 Nissan Motor Co., Ltd. Internal combustion engine equipped with fuel reforming system
US6334424B1 (en) * 1999-03-05 2002-01-01 Toyota Jidosha Kabushiki Kaisha Control device and control method for vehicle
US6336320B1 (en) * 1998-07-10 2002-01-08 Toyota Jidosha Kabushiki Kaisha Exhaust gas purification device for an internal combustion engine
US6349702B1 (en) * 1999-09-20 2002-02-26 Isuzu Motors Limited Common-rail fuel-injection system
US6390030B1 (en) * 1999-06-03 2002-05-21 Toyota Jidosha Kabushiki Kaisha Fuel reformer for mounting on a vehicle
US6536209B2 (en) * 2001-06-26 2003-03-25 Caterpillar Inc Post injections during cold operation
US6591817B2 (en) * 2001-03-21 2003-07-15 Motorola, Inc. Dual fuel method and system
US6666020B2 (en) * 2001-08-03 2003-12-23 C.R.F. Societa Consortile Per Azioni Method of initiating regeneration of a particulate filter for a direct-injection diesel engine with a common rail injection system
US6705295B1 (en) * 1999-10-08 2004-03-16 Renault Method for measuring the fuel pressure in an injection train of an internal combustion engine
US6711893B2 (en) * 2001-03-27 2004-03-30 Toyota Jidosha Kabushiki Kaisha Fuel supply apparatus for an internal combustion engine
US6729301B2 (en) * 2002-06-11 2004-05-04 Mitsubishi Jidosha Kogyo Kabushiki Kaisha Ignition timing control system for internal combustion engine
US6751543B2 (en) * 2000-10-10 2004-06-15 Robert Bosch Gmbh Method, computer program, and control system for operating a motor vehicle having an internal combustion engine
US20040139944A1 (en) * 2003-01-06 2004-07-22 Hitachi, Ltd. Method and device for controlling fuel injection in the bi-fuel internal combustion engine
US6843055B2 (en) * 2001-06-22 2005-01-18 Nissan Motor Co., Ltd. Regeneration of diesel particulate filter for diesel engine
US6851398B2 (en) * 2003-02-13 2005-02-08 Arvin Technologies, Inc. Method and apparatus for controlling a fuel reformer by use of existing vehicle control signals
US6872365B1 (en) * 1999-05-19 2005-03-29 Daimlerchrysler Ag Exhaust gas cleaning system having internal ammonia production for reducing nitrogen oxides
US6964261B2 (en) * 2003-12-11 2005-11-15 Perkins Engines Company Limited Adaptive fuel injector trimming during a zero fuel condition
US6988481B2 (en) * 2003-05-16 2006-01-24 Honda Motor Co., Ltd. Control system for cylinder cut-off internal combustion engine
US6990956B2 (en) * 2003-08-07 2006-01-31 Toyota Jidosha Kabushiki Kaisha Internal combustion engine
US6997142B2 (en) * 2003-01-28 2006-02-14 Toyota Jidosha Kabushiki Kaisha Internal combustion engine and method of operating internal combustion engine
US7017339B2 (en) * 2004-03-12 2006-03-28 Daimlerchrysler Corporation Exhaust system catalyst assembly for a dual crankshaft engine
US20060096275A1 (en) * 2004-11-08 2006-05-11 Caterpillar Inc. Exhaust purification with on-board ammonia production
US7047940B2 (en) * 2003-11-20 2006-05-23 Toyota Jidosha Kabushiki Kaisha Control apparatus and control method for internal combustion engine
US7089888B2 (en) * 2004-12-30 2006-08-15 Council Of Scientific And Industrial Research Device for production of hydrogen from effluents of internal combustion engines
US7104244B2 (en) * 2004-11-22 2006-09-12 Honda Motor Co., Ltd. Control system for variable-cylinder internal combustion engine
US7159541B2 (en) * 2003-08-27 2007-01-09 Toyota Jidosha Kabushiki Kaisha Method and apparatus for determining state of reformer
US7203579B2 (en) * 2001-12-21 2007-04-10 Kabushiki Kaisha Bridgestone Method and apparatus for estimating road surface state and tire running state, ABS and vehicle control using the same
US7216480B2 (en) * 2003-01-23 2007-05-15 Toyota Jidosha Kabushiki Kaisha Exhaust emission control system
US7228841B2 (en) * 2004-11-12 2007-06-12 Mazada Motor Corporation Fuel switching for dual fuel engine
US7261065B2 (en) * 2005-02-17 2007-08-28 Honda Motor Co., Ltd. Method for controlling compression ignition internal combustion engine
US20080010993A1 (en) * 2006-06-13 2008-01-17 Monsanto Technology Llc Reformed alcohol power systems
US20080098985A1 (en) * 2006-10-30 2008-05-01 Honda Motor Co., Ltd. Internal combustion engine system
US7370609B2 (en) * 2006-03-23 2008-05-13 Honda Motor Co., Ltd. Internal combustion engine system
US20080141984A1 (en) * 2004-07-28 2008-06-19 Nissan Motor Co., Ltd. Fuel Supply System
US20080221778A1 (en) * 2007-03-09 2008-09-11 Nissan Motor Co., Ltd. Control device for internal combustion engine
US20080228375A1 (en) * 2007-03-12 2008-09-18 Nissan Motor Co., Ltd. Spark ignition type internal combustion engine
US20080282998A1 (en) * 2007-05-17 2008-11-20 Honda Motor Co., Ltd. Ethanol fuel reforming system for internal combustion engines
US7454898B2 (en) * 2004-12-28 2008-11-25 Robert Bosch Gmbh Vehicle with a supply unit
US20090017987A1 (en) * 2007-07-10 2009-01-15 Hitachi, Ltd. Control Method and Control Device for Engine
US20090030588A1 (en) * 2007-07-23 2009-01-29 Denso Corporation Controller for internal combustion engine
US20090043479A1 (en) * 2007-08-06 2009-02-12 Nissan Motor Co., Ltd. Internal combustion engine
US20090065409A1 (en) * 2007-09-06 2009-03-12 Honda Motor Co., Ltd. Gasoline-ethanol separation apparatus
US20090071453A1 (en) * 2007-09-14 2009-03-19 William Francis Stockhausen Bi-fuel Engine Using Hydrogen
US7523744B2 (en) * 2005-10-27 2009-04-28 Nissan Motor Co., Ltd. Apparatus and method for controlling an internal combustion engine
US7530335B2 (en) * 2005-08-03 2009-05-12 Toyota Jidosha Kabushiki Kaisha Internal combustion engine and starting control device of internal combustion engine

Family Cites Families (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4335171C1 (en) * 1993-10-15 1995-05-04 Daimler Benz Ag Fuel injection system for a multi-cylinder diesel internal combustion engine
JP4552694B2 (en) * 2005-03-02 2010-09-29 トヨタ自動車株式会社 Vehicle fuel supply device
JP4449956B2 (en) 2006-08-04 2010-04-14 トヨタ自動車株式会社 Internal combustion engine
JP4840288B2 (en) * 2006-11-14 2011-12-21 株式会社デンソー Fuel injection apparatus and adjustment method thereof
US7717088B2 (en) * 2007-05-07 2010-05-18 Ford Global Technologies, Llc Method of detecting and compensating for injector variability with a direct injection system
GB2449706A (en) * 2007-06-01 2008-12-03 Scania Cv Ab Identifying a Malfunctioning Fuel Injector
US7543485B2 (en) * 2007-06-12 2009-06-09 Gm Global Technology Operations, Inc. Onboard fuel injector test
DE102007028900B4 (en) * 2007-06-22 2013-06-27 Continental Automotive Gmbh Method and device for diagnosing an injection valve of an internal combustion engine that is in communication with a fuel rail
US7802562B2 (en) * 2008-07-31 2010-09-28 Ford Global Technologies, Llc Engine boost control for multi-fuel engine
US8245671B2 (en) 2010-04-08 2012-08-21 Ford Global Technologies, Llc Operating an engine with reformate
US8307790B2 (en) 2010-04-08 2012-11-13 Ford Global Technologies, Llc Method for operating a vehicle with a fuel reformer
US8015952B2 (en) 2010-04-08 2011-09-13 Ford Global Technologies, Llc Engine fuel reformer monitoring
US8539914B2 (en) 2010-04-08 2013-09-24 Ford Global Technologies, Llc Method for operating an engine with a fuel reformer
US8001934B2 (en) 2010-04-08 2011-08-23 Ford Global Technologies, Llc Pump control for reformate fuel storage tank
US8402928B2 (en) 2010-04-08 2013-03-26 Ford Global Technologies, Llc Method for operating an engine with variable charge density
US8146541B2 (en) 2010-04-08 2012-04-03 Ford Global Technologies, Llc Method for improving transient engine operation
US8230826B2 (en) 2010-04-08 2012-07-31 Ford Global Technologies, Llc Selectively storing reformate
US8191514B2 (en) 2010-04-08 2012-06-05 Ford Global Technologies, Llc Ignition control for reformate engine
US8041500B2 (en) 2010-04-08 2011-10-18 Ford Global Technologies, Llc Reformate control via accelerometer
US8613263B2 (en) 2010-04-08 2013-12-24 Ford Global Technologies, Llc Method for operating a charge diluted engine
US8037850B2 (en) 2010-04-08 2011-10-18 Ford Global Technologies, Llc Method for operating an engine

Patent Citations (68)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5176122A (en) * 1990-11-30 1993-01-05 Toyota Jidosha Kabushiki Kaisha Fuel injection device for an internal combustion engine
US5224452A (en) * 1991-09-12 1993-07-06 Japan Electronic Control Systems Co., Ltd. Air-fuel ratio control system of internal combustion engine
US5372411A (en) * 1992-04-13 1994-12-13 Robert Bosch Gmbh Safety equipment for a motor vehicle
US5445019A (en) * 1993-04-19 1995-08-29 Ford Motor Company Internal combustion engine with on-board diagnostic system for detecting impaired fuel injectors
US5526797A (en) * 1994-01-07 1996-06-18 Stokes; Richard A. Methods and apparatus for vaporizing and utilizing fuels of various octane ratings
US5528901A (en) * 1994-03-01 1996-06-25 Auxiliary Power Dynamics, Inc. Compact auxiliary power system for heavy-duty diesel engines and method
US5542394A (en) * 1994-04-15 1996-08-06 Unisia Jecs Corporation Vehicle engine refueling detection apparatus and method and fuel supply apparatus and method
US5740667A (en) * 1994-12-15 1998-04-21 Amoco Corporation Process for abatement of nitrogen oxides in exhaust from gas turbine power generation
US5682864A (en) * 1995-08-01 1997-11-04 Nissan Motor Co., Ltd. Controller for internal combustion engines
US5857445A (en) * 1995-08-24 1999-01-12 Hitachi, Ltd. Engine control device
US6047542A (en) * 1995-11-17 2000-04-11 Toyota Jidosha Kabushiki Kaisha Method and device for purifying exhaust gas of engine
US6247449B1 (en) * 1995-12-22 2001-06-19 Ab Volvo Method for reducing vibration in a vehicle and a device for accomplishment of the method
US5762366A (en) * 1995-12-29 1998-06-09 Autoliv Asp, Inc. Safety system
US5633458A (en) * 1996-01-16 1997-05-27 Ford Motor Company On-board fuel delivery diagnostic system for an internal combustion engine
US6213104B1 (en) * 1996-02-14 2001-04-10 Toyota Jidosha Kabushiki Kaisha Method and a device for supplying fuel to an internal combustion engine
US5964088A (en) * 1996-03-22 1999-10-12 Toyota Jidosha Kabushiki Kaisha Device for purifying exhaust gas of engine
US6024069A (en) * 1997-06-02 2000-02-15 Nissan Motor Co., Ltd. Controller for an internal combustion engine
US6058906A (en) * 1997-07-02 2000-05-09 Nissan Motor Co., Ltd. Fuel/air ratio control for internal combustion engine
US6176215B1 (en) * 1997-07-18 2001-01-23 Daimler Benz Aktiengesellschaft Method for operation of a direct-injection spark-ignition internal combustion engine
US6088647A (en) * 1997-09-16 2000-07-11 Daimlerchrysler Ag Process for determining a fuel-injection-related parameter for an internal-combustion engine with a common-rail injection system
US6336320B1 (en) * 1998-07-10 2002-01-08 Toyota Jidosha Kabushiki Kaisha Exhaust gas purification device for an internal combustion engine
US6289672B1 (en) * 1998-07-21 2001-09-18 Toyota Jidosha Kabushiki Kaisha Exhaust gas purification device for an internal combustion engine
US6334424B1 (en) * 1999-03-05 2002-01-01 Toyota Jidosha Kabushiki Kaisha Control device and control method for vehicle
US6318306B1 (en) * 1999-04-06 2001-11-20 Nissan Motor Co., Ltd. Internal combustion engine equipped with fuel reforming system
US6872365B1 (en) * 1999-05-19 2005-03-29 Daimlerchrysler Ag Exhaust gas cleaning system having internal ammonia production for reducing nitrogen oxides
US6244043B1 (en) * 1999-05-19 2001-06-12 Ford Global Technologies, Inc. Emission control device air/fuel ratio control system
US6390030B1 (en) * 1999-06-03 2002-05-21 Toyota Jidosha Kabushiki Kaisha Fuel reformer for mounting on a vehicle
US6349702B1 (en) * 1999-09-20 2002-02-26 Isuzu Motors Limited Common-rail fuel-injection system
US6705295B1 (en) * 1999-10-08 2004-03-16 Renault Method for measuring the fuel pressure in an injection train of an internal combustion engine
US20010003977A1 (en) * 1999-12-13 2001-06-21 Kenji Hayashi Fuel injection system for internal combustion engines and its method of control
US6751543B2 (en) * 2000-10-10 2004-06-15 Robert Bosch Gmbh Method, computer program, and control system for operating a motor vehicle having an internal combustion engine
US6591817B2 (en) * 2001-03-21 2003-07-15 Motorola, Inc. Dual fuel method and system
US6711893B2 (en) * 2001-03-27 2004-03-30 Toyota Jidosha Kabushiki Kaisha Fuel supply apparatus for an internal combustion engine
US6843055B2 (en) * 2001-06-22 2005-01-18 Nissan Motor Co., Ltd. Regeneration of diesel particulate filter for diesel engine
US6536209B2 (en) * 2001-06-26 2003-03-25 Caterpillar Inc Post injections during cold operation
US6666020B2 (en) * 2001-08-03 2003-12-23 C.R.F. Societa Consortile Per Azioni Method of initiating regeneration of a particulate filter for a direct-injection diesel engine with a common rail injection system
US7203579B2 (en) * 2001-12-21 2007-04-10 Kabushiki Kaisha Bridgestone Method and apparatus for estimating road surface state and tire running state, ABS and vehicle control using the same
US6729301B2 (en) * 2002-06-11 2004-05-04 Mitsubishi Jidosha Kogyo Kabushiki Kaisha Ignition timing control system for internal combustion engine
US20040139944A1 (en) * 2003-01-06 2004-07-22 Hitachi, Ltd. Method and device for controlling fuel injection in the bi-fuel internal combustion engine
US7216480B2 (en) * 2003-01-23 2007-05-15 Toyota Jidosha Kabushiki Kaisha Exhaust emission control system
US6997142B2 (en) * 2003-01-28 2006-02-14 Toyota Jidosha Kabushiki Kaisha Internal combustion engine and method of operating internal combustion engine
US6851398B2 (en) * 2003-02-13 2005-02-08 Arvin Technologies, Inc. Method and apparatus for controlling a fuel reformer by use of existing vehicle control signals
US6988481B2 (en) * 2003-05-16 2006-01-24 Honda Motor Co., Ltd. Control system for cylinder cut-off internal combustion engine
US6990956B2 (en) * 2003-08-07 2006-01-31 Toyota Jidosha Kabushiki Kaisha Internal combustion engine
US7159541B2 (en) * 2003-08-27 2007-01-09 Toyota Jidosha Kabushiki Kaisha Method and apparatus for determining state of reformer
US7047940B2 (en) * 2003-11-20 2006-05-23 Toyota Jidosha Kabushiki Kaisha Control apparatus and control method for internal combustion engine
US6964261B2 (en) * 2003-12-11 2005-11-15 Perkins Engines Company Limited Adaptive fuel injector trimming during a zero fuel condition
US7017339B2 (en) * 2004-03-12 2006-03-28 Daimlerchrysler Corporation Exhaust system catalyst assembly for a dual crankshaft engine
US20080141984A1 (en) * 2004-07-28 2008-06-19 Nissan Motor Co., Ltd. Fuel Supply System
US20060096275A1 (en) * 2004-11-08 2006-05-11 Caterpillar Inc. Exhaust purification with on-board ammonia production
US7228841B2 (en) * 2004-11-12 2007-06-12 Mazada Motor Corporation Fuel switching for dual fuel engine
US7104244B2 (en) * 2004-11-22 2006-09-12 Honda Motor Co., Ltd. Control system for variable-cylinder internal combustion engine
US7454898B2 (en) * 2004-12-28 2008-11-25 Robert Bosch Gmbh Vehicle with a supply unit
US7089888B2 (en) * 2004-12-30 2006-08-15 Council Of Scientific And Industrial Research Device for production of hydrogen from effluents of internal combustion engines
US7261065B2 (en) * 2005-02-17 2007-08-28 Honda Motor Co., Ltd. Method for controlling compression ignition internal combustion engine
US7530335B2 (en) * 2005-08-03 2009-05-12 Toyota Jidosha Kabushiki Kaisha Internal combustion engine and starting control device of internal combustion engine
US7523744B2 (en) * 2005-10-27 2009-04-28 Nissan Motor Co., Ltd. Apparatus and method for controlling an internal combustion engine
US7370609B2 (en) * 2006-03-23 2008-05-13 Honda Motor Co., Ltd. Internal combustion engine system
US20080010993A1 (en) * 2006-06-13 2008-01-17 Monsanto Technology Llc Reformed alcohol power systems
US20080098985A1 (en) * 2006-10-30 2008-05-01 Honda Motor Co., Ltd. Internal combustion engine system
US20080221778A1 (en) * 2007-03-09 2008-09-11 Nissan Motor Co., Ltd. Control device for internal combustion engine
US20080228375A1 (en) * 2007-03-12 2008-09-18 Nissan Motor Co., Ltd. Spark ignition type internal combustion engine
US20080282998A1 (en) * 2007-05-17 2008-11-20 Honda Motor Co., Ltd. Ethanol fuel reforming system for internal combustion engines
US20090017987A1 (en) * 2007-07-10 2009-01-15 Hitachi, Ltd. Control Method and Control Device for Engine
US20090030588A1 (en) * 2007-07-23 2009-01-29 Denso Corporation Controller for internal combustion engine
US20090043479A1 (en) * 2007-08-06 2009-02-12 Nissan Motor Co., Ltd. Internal combustion engine
US20090065409A1 (en) * 2007-09-06 2009-03-12 Honda Motor Co., Ltd. Gasoline-ethanol separation apparatus
US20090071453A1 (en) * 2007-09-14 2009-03-19 William Francis Stockhausen Bi-fuel Engine Using Hydrogen

Cited By (27)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8360015B2 (en) 2010-04-08 2013-01-29 Ford Global Technologies, Llc Engine fuel reformer monitoring
US9932912B2 (en) * 2011-03-04 2018-04-03 General Electric Company Methods and systems for emissions control in a dual fuel engine
US20120222400A1 (en) * 2011-03-04 2012-09-06 General Electric Company Methods and systems for emissions control in a dual fuel engine
US8601863B2 (en) * 2011-03-25 2013-12-10 Toyota Jidosha Kabushiki Kaisha Abnormality determination apparatus and abnormality determination method for multi-cylinder internal combustion engine
US20120240669A1 (en) * 2011-03-25 2012-09-27 Denso Corporation Abnormality determination apparatus and abnormality determination method for multi-cylinder internal combustion engine
US9695756B2 (en) 2011-11-30 2017-07-04 Aisan Kogyo Kabushiki Kaisha Fuel supply control apparatus for bi-fuel internal combustion engine, and method of switching fuel in bi-fuel internal combustion engine
EP2787200A4 (en) * 2011-11-30 2016-03-30 Aisan Ind Fuel supply control apparatus for bi-fuel internal combustion engine, and method of switching fuel in bi-fuel internal combustion engine
US20130151114A1 (en) * 2011-12-09 2013-06-13 Hyundai Motor Company Method of managing auxiliary fuel system for ffv
US10450193B2 (en) 2012-03-30 2019-10-22 Monsanto Technology Llc Alcohol reformer for reforming alcohol to mixture of gas including hydrogen
US9347386B2 (en) 2012-03-30 2016-05-24 Monsanto Technology Llc Alcohol reforming system for internal combustion engine
EP2653706A1 (en) * 2012-04-20 2013-10-23 Caterpillar Motoren GmbH & Co. KG Monitoring the fuel injection system of dual fuel engines
WO2013156161A1 (en) 2012-04-20 2013-10-24 Caterpillar Motoren Gmbh & Co. Kg Monitoring ignition fuel injection systems of dual fuel engines
US20140238353A1 (en) * 2013-02-27 2014-08-28 Caterpillar Inc. Apparatus and Method for Detecting Leakage of Liquid Fuel into Gas Fuel Rail
US9453476B2 (en) * 2013-03-28 2016-09-27 Ford Global Technologies, Llc Method for operating a direct fuel injector
US20140290597A1 (en) * 2013-03-28 2014-10-02 Ford Global Technologies, Llc Method for operating a direct fuel injector
US20150211432A1 (en) * 2013-03-28 2015-07-30 Ford Global Technologies, Llc Method for operating a direct fuel injector
US8997714B2 (en) * 2013-03-28 2015-04-07 Ford Global Technologies, Llc Method for operating a direct fuel injector
US9850842B2 (en) * 2013-04-19 2017-12-26 Liebherr Machines Bulle Sa Controller for a common-rail injection system
US20140311453A1 (en) * 2013-04-19 2014-10-23 Liebherr Machines Bulle Sa Controller for a Common-Rail Injection System
EP2999879A4 (en) * 2013-05-23 2017-02-15 Scania CV AB Method and device for operation of a high pressure fuel pump
US9863386B2 (en) 2013-05-23 2018-01-09 Scania Cv Ab Method and device for operation of a high pressure fuel pump
EP2853713A3 (en) * 2013-09-26 2016-03-23 Man Diesel & Turbo, Filial Af Man Diesel & Turbo Se, Tyskland A large low-speed tubocharged two-stroke internal combustion engine with a dual fuel supply system
US9824505B2 (en) * 2014-02-25 2017-11-21 Ford Global Technologies, Llc Method for triggering a vehicle system monitor
US20150243109A1 (en) * 2014-02-25 2015-08-27 Ford Global Technologies, Llc Method for triggering a vehicle system monitor
RU2701430C2 (en) * 2014-09-18 2019-09-26 Форд Глобал Текнолоджиз, Ллк Method of determining fuel injector operation characteristic
US11873776B1 (en) * 2022-08-02 2024-01-16 Caterpillar Inc. Fuel injector drive system
US20240044298A1 (en) * 2022-08-02 2024-02-08 Caterpillar Inc. Fuel injector drive system

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